Magnetic refrigeration system and vehicle air conditioning device

ABSTRACT

A magnetic refrigeration system constructed in such a way that a refrigerant transfer part transfers refrigerant from a first refrigerant discharge part of one refrigerant port to a first refrigerant circulation circuit after a magnetic field is applied to a magnetic working material by a magnetic field applying and removing part and that the refrigerant transfer part transfers refrigerant from a second refrigerant discharge part of other refrigerant port to a second refrigerant circulation circuit after the magnetic field is removed from the magnetic working material by the magnetic field applying and removing part.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present disclosure is based on Japanese Patent Application No.2011-14914 filed on Jan. 27, 2011, Japanese Patent Application No.2011-110206 filed on May 17, 2011, and Japanese Patent Application No.2011-281288 filed on Dec. 22, 2011, and the contents of those areincorporated herein by reference in their entirety.

TECHNICAL FIELD

The present disclosure relates to a magnetic refrigeration system and avehicle air conditioning device to which the magnetic refrigerationsystem is applied.

BACKGROUND ART

There is proposed a magnetic refrigeration system utilizing a phenomenon(magnetocaloric effect) such that when a magnetic field is applied to amagnetic working material such as a magnetic material, the magneticworking material generates heat and such that when the magnetic field isremoved from the magnetic working material, the magnetic workingmaterial is decreased in temperature (see, for example, patent document1).

The magnetic refrigeration system of this patent document 1 isconstructed of: a magnetic working material mounted in a railroadvehicle; a strong magnetic field generating device for applying amagnetic field to the magnetic working material; a first heat exchangeflow passage through which a heating medium for transferring the heat(hot heat) of the magnetic working material flows, the heat (hot heat)being increased when the magnetic field applied to the magnetic workingmaterial by the strong magnetic field generating device is increased; asecond heat exchange flow passage through which the heating medium fortransferring the heat (cold heat) of the magnetic working materialflows, the heat (cold heat) being decreased when the magnetic fieldapplied to the magnetic material by the strong magnetic field generatingdevice is decreased; and pumps and heat exchangers arranged in therespective heat exchange flow passages.

When the magnetic field applied by the strong magnetic field generatingdevice is increased, the pump disposed in the first heat exchange flowpassage is activated to make the heating medium whose temperature isincreased by the hot heat of the magnetic working material exchange heatwith air outside a passenger compartment by the heat exchanger. On theother hand, when the magnetic field applied by the strong magnetic fieldgenerating device is decreased, the pump disposed in the second heatexchange flow passage is activated to make the heating medium whosetemperature is decreased by the cold heat of the magnetic workingmaterial exchange heat with air inside the passenger compartment by theheat exchanger.

By the way, in the magnetic refrigeration system of the patent document1, the strong magnetic field generating device is constructed of asuperconducting coil or the like so as to increase a temperature changein the magnetic working material and the application of the magneticrefrigeration system is limited to special uses. Hence, it is difficultto apply the magnetic refrigeration system to a general-purpose productsuch as a vehicle air conditioning device.

As a means for solving an issue like this has been known an AMR (ActiveMagnetic Refrigerator) type magnetic refrigeration system in which:after a magnetic field applied to a magnetic working material isincreased, refrigerant (magnetic heat transporting medium) istransferred to one end (high temperature end) in the magnetic workingmaterial; and after the magnetic field applied to the magnetic workingmaterial is decreased, the refrigerant is transferred to the other end(low temperature end) in the magnetic working material, whereby the coldheat and the hot heat generated by the magnetocaloric effect are storedin the magnetic working material itself.

The AMR type magnetic refrigeration system generally has a containerfilled with a magnetic working material and having a refrigerant flowpassage through which a refrigerant flows and reciprocally transfers therefrigerant between one end and the other end of the container accordingto applying and removing a magnetic field to and from the magneticworking material.

The following four processes are repeated: (i) applying the magneticfield to the magnetic working material; (ii) transporting hot heatgenerated in the magnetic working material to the one end (hightemperature end) of the container by the refrigerant; (iii) removing themagnetic field from the magnetic working material; and (iv) transportingcold heat generated in the magnetic working material to the other end(low temperature end) of the container by the refrigerant.

In this way, a temperature gradient is produced in the magnetic workingmaterial in the container and hence a large temperature difference isproduced between a high temperature end and a low temperature end in thecontainer.

Here, it may be thought that the AMR type magnetic refrigeration systemis applicable to the magnetic refrigeration system of the patentdocument 1. However, in this case, there is presented an issue that theCOP (Coefficient Of Performance) of refrigeration of the magneticrefrigeration system is reduced. Here, the COP expresses a cooling orheating capacity per 1 kW of power consumption.

This is because a refrigerant flowing through a refrigerant flow passageis made to exchange heat with a heating medium flowing through a heatexchange flow passage, around a magnetic working material, in the casewhere the AMR type magnetic refrigeration system is applied to themagnetic refrigeration system of the patent document 1. Hence the heatof the magnetic working material is transmitted indirectly to theheating medium flowing through the heat exchange flow passage. At thistime, a heat exchange loss is increased between the magnetic workingmaterial and the heating medium.

PRIOR ART DOCUMENT Patent Document

-   Patent document 1: JP-A-2006-56274

SUMMARY OF THE INVENTION

An object of the present disclosure is to provide a magneticrefrigeration system and a vehicle air conditioning device to which themagnetic refrigeration system is applied.

A magnetic refrigeration system according to one example of the presentdisclosure is provided with: a cylindrical container having a pluralityof working chambers formed therein radially in a circumferentialdirection, the plurality of working chambers having a magnetic workingmaterial having a magnetocaloric effect arranged therein and havingrefrigerant flowing therethrough; a magnetic field applying and removingpart which repeats applying and removing a magnetic field to and fromthe magnetic working material; a first refrigerant circulation circuitconstructed in such a way that the refrigerant flowing out of arefrigerant discharge part of one refrigerant port flows through a firstheat exchanger and returns to a refrigerant suction part of the onerefrigerant port, of the one and other refrigerant ports respectivelydisposed on end faces of the container in a longitudinal direction; asecond refrigerant circulation circuit constructed in such a way thatthe refrigerant flowing out of a refrigerant discharge part of the otherrefrigerant port flows through a second heat exchanger and returns to arefrigerant suction part of the other refrigerant port, of the one andthe other refrigerant ports; and a refrigerant transfer part whichtransfers the refrigerant between the one refrigerant port and the otherrefrigerant port, wherein after the magnetic field is applied to themagnetic working material by the magnetic field applying and removingpart, the refrigerant transfer part transfers the refrigerant from theother refrigerant port to the one refrigerant port, and wherein afterthe magnetic field is removed from the magnetic working material by themagnetic field applying and removing part, the refrigerant transfer parttransfers the refrigerant from the one refrigerant port to the otherrefrigerant port.

Accordingly, after the magnetic field is applied to the magnetic workingmaterial, the refrigerant is transferred from the other refrigerant portto the one refrigerant port in the working chambers, whereby therefrigerant near the one refrigerant port, whose temperature isincreased by hot heat of the magnetic working material generated byapplying the magnetic field to the magnetic working material, can bemade to flow into the first heat exchanger via the first refrigerantcirculation circuit.

Further, after the magnetic field is removed from the magnetic workingmaterial, the refrigerant is transferred from the one refrigerant portto the other refrigerant port in the working chambers, whereby therefrigerant near the other refrigerant port, whose temperature isdecreased by cold heat of the magnetic working material generated byremoving the magnetic field from the magnetic working material, can bemade to flow into the second heat exchanger via the second refrigerantcirculation circuit.

In this way, the refrigerant whose temperature is increased by the hotheat generated in the magnetic working material can be made to flowdirectly into the first heat exchanger and the refrigerant whosetemperature is decreased by the cold heat generated in the magneticworking material can be made to flow directly into the second heatexchanger. Hence, a heat exchange loss can be reduced when the hot heatand the cold heat generated in the magnetic working material aretransported, and hence the COP of the magnetic refrigeration system canbe improved.

In this regard, when the refrigerant is transferred from the otherrefrigerant port to the one refrigerant port in the working chambers, itfollows that the refrigerant flowing through the second heat exchangerflows into the working chambers via the other refrigerant port from thesecond refrigerant circulation circuit. Further, when the refrigerant istransferred from the one refrigerant port to the other refrigerant portin the working chambers, it follows that the refrigerant flowing throughthe first heat exchanger flows into the working chambers via the onerefrigerant port from the first refrigerant circulation circuit.

In particular, by making the volume of a space constructing each of therefrigerant suction part and the refrigerant discharge part smaller thanthe volume of the refrigerant discharged at one time in the refrigeranttransfer part, it is possible to prevent the refrigerant, whosetemperature is increased by the hot heat generated in the magneticworking material, and the refrigerant, whose temperature is decreased bythe cold heat generated in the magnetic working material, from remainingin the container. In other words, it is possible to efficientlydischarge the refrigerant, whose temperature is increased by the hotheat generated in the magnetic working material, and the refrigerant,whose temperature is decreased by the cold heat generated in themagnetic working material, to the outside.

Further, the refrigerant suction part is provided with a suction valveopened when the refrigerant is sucked into the working chambers, and therefrigerant discharge part is provided with a discharge valve openedwhen the refrigerant is discharged from the working chambers.

According to this, after the magnetic field is applied to the magneticworking material, the refrigerant near the one refrigerant port, whosetemperature is increased by the hot heat generated in the magneticworking material by applying the magnetic field, can be made to surelyflow into the first heat exchanger via the first refrigerant circulationcircuit and the refrigerant flowing out of the second heat exchanger canbe sucked into the working chambers from the other refrigerant port.

Further, after the magnetic field is removed from the magnetic workingmaterial, the refrigerant near the other refrigerant port, whosetemperature is decreased by the cold heat generated in the magneticworking material by removing the magnetic field, can be made to surelyflow into the second heat exchanger via the second refrigerantcirculation circuit and the refrigerant flowing out of the first heatexchanger can be sucked into the working chambers from the onerefrigerant port.

Still further, the discharge valve is arranged at a position nearer tothe working chambers than the suction valve is in the longitudinaldirection of the container.

In this way, when the discharge valve is arranged in the vicinity of theworking chambers, it is possible to prevent an unnecessary heat exchangebetween the refrigerant remaining around the suction valve and therefrigerant discharged from the working chambers via the dischargevalve. This can reduce a heat exchange loss when the hot heat and thecold heat generated in the magnetic working material are transported,and hence can improve the COP of the magnetic refrigeration system.

Still further, of the suction valve and the discharge valve, at leastthe suction valve is constructed of a rotary valve having a valve plateand a rotary disk, the valve plate being arranged adjacently to theworking chambers and having a communication hole communicating with aninterior of the working chambers, the rotary disk rotating in acircumferential direction of the container to thereby open or close thecommunication hole.

According to this, it is possible to prevent the refrigerant fromremaining around the suction valve and to prevent an unnecessary heatexchange between the refrigerant remaining around the suction valve andthe refrigerant discharged from the working chambers via the dischargevalve. This can reduce a heat exchange loss when the hot heat and thecold heat generated in the magnetic working material are transported,and hence can improve the COP of the magnetic refrigeration system.

Still further, when the rotary valve is constructed in such a way thatthe rotary disk rotates by the use of power for driving the magneticfield applying and removing part, the magnetic refrigeration system canbe realized by a simple construction.

Still further, each of the refrigerant suction part and the refrigerantdischarge part in the one refrigerant port is provided with a firstbackward flow preventing part for allowing the refrigerant to flow inone direction in order of the refrigerant discharge part, a refrigerantflow-in port in the first heat exchanger, a refrigerant flow-out port inthe first heat exchanger, and the refrigerant suction part, and each ofthe refrigerant suction part and the refrigerant discharge part in theother refrigerant port is provided with a second backward flowpreventing part for allowing the refrigerant to flow in one direction inorder of the refrigerant discharge part, a refrigerant flow-in port inthe second heat exchanger, a refrigerant flow-out port in the secondheat exchanger, and the refrigerant suction part.

This can also make the refrigerant near the one refrigerant port, whosetemperature is increased by the hot heat generated in the magneticworking material by applying the magnetic field after the magnetic fieldis applied to the magnetic working material, surely flows into the firstheat exchanger via the first refrigerant circulation circuit and cansuck the refrigerant flowing out of the second heat exchanger into theworking chambers from the other refrigerant port.

Further, this can make the refrigerant near the other refrigerant port,whose temperature is decreased by the cold heat generated in themagnetic working material by removing the magnetic field after themagnetic field is removed from the magnetic working material, surelyflows into the second heat exchanger via the second refrigerantcirculation circuit and can suck the refrigerant flowing out of thefirst heat exchanger into the working chambers from the one refrigerantport.

Still further, when at least one of the first backward flow preventingpart and the second backward flow preventing part is constructed of afluid diode in which resistance is smaller in a forward direction of aflow of the refrigerant than in a backward direction of the flow of therefrigerant, the magnetic refrigeration system can be realized by asimple construction.

Still further, when the refrigerant suction part and the refrigerantdischarge part are disposed plurally in correspondence to the pluralityof working chambers, it is preferable that the refrigerant suction partsare disposed in such a way as to be positioned on a same circumferencewhen viewed from the longitudinal direction of the container and thatthe refrigerant discharge parts are disposed in such a way as to bepositioned on a same circumference when viewed from the longitudinaldirection of the container.

Specifically, the magnetic field applying and removing part isconstructed of a magnetic field generating part, a rotary shaft forrotatably supporting the magnetic field generating part, and a drivepart for driving the rotary shaft, and the magnetic field generatingpart is disposed in such a way as to periodically come near to themagnetic working material according to the rotation of the rotary shaft.This makes it possible to periodically repeat applying and removing themagnetic field to and from the magnetic working material by the magneticfield applying and removing part.

Still further, the magnetic refrigeration system is provided with apower transmission mechanism for transmitting power by the drive part tothe refrigerant transfer part. The refrigerant transfer partreciprocally transfers the refrigerant between the one refrigerant portand the other refrigerant port by the power transmitted via the powertransmission mechanism.

In this way, when the magnetic refrigeration system employs aconstruction in which the refrigerant transfer part is driven by thepower of the drive part of the magnetic field applying and removingpart, the drive source can be common between the refrigerant transferpart and the magnetic field applying and removing part. Hence, themagnetic refrigeration system can be realized by a simple construction.Moreover, power consumption in the magnetic refrigeration system can berestricted from increasing, and hence can further improve the COP of themagnetic refrigeration system.

Still further, it is preferable that the refrigerant transfer part isconstructed of a multi-cylinder type piston pump having a plurality ofcylinders and a plurality of pistons, corresponding to the plurality ofworking chambers.

Still further, when a vehicle air conditioning device to which themagnetic refrigeration system described above is applied includes a caseconstructing an air flow passage for blown air to be blown into apassenger compartment. A heating heat exchanger for heating the blow airto be blown into the passenger compartment is constructed by the firstheat exchanger, and a cooling heat exchanger for cooling the blow air tobe blown into the passenger compartment is constructed by the secondheat exchanger. Thus, the vehicle air conditioning device can cool andheat the interior of the passenger compartment.

Specifically, when the first heat exchanger is arranged downstream ofthe second heat exchanger in a flow of the blown air in the case, thefirst heat exchanger can heat the blown air, which is cooled anddehumidified by the second heat exchanger, thereby dehumidify the blownair at the time of heating the interior of the passenger compartment.

Still further, the vehicle air conditioning device may include atemperature adjusting part for adjusting a volume of the blown airflowing into the first heat exchanger to thereby adjust a temperature ofair blown off into the passenger compartment.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-mentioned object and other objects, features, and advantagesof the present disclosure will be made clear by the following detaileddescriptions with reference to the accompanying drawings.

FIG. 1 is a general construction diagram illustrating a vehicle airconditioning device according to a first embodiment.

FIG. 2 is an enlarged view illustrating a magnetic refrigeratoraccording to the first embodiment.

FIG. 3 is a section view taken along a line A-A in FIG. 2.

FIG. 4 is an explanatory view illustrating an operating principle of themagnetic refrigerator according to the first embodiment.

FIG. 5 is a general construction diagram illustrating a refrigerantcircuit at the time of a cooling mode of the vehicle air conditioningdevice according to the first embodiment.

FIG. 6 is a general construction diagram illustrating the refrigerantcircuit at the time of a heating mode of the vehicle air conditioningdevice according to the first embodiment.

FIG. 7 is a general construction diagram illustrating the refrigerantcircuit at the time of a dehumidifying mode of the vehicle airconditioning device according to the first embodiment.

FIG. 8 is a general construction diagram illustrating a vehicle airconditioning device according to a second embodiment.

FIG. 9 is a general construction diagram illustrating a vehicle airconditioning device according to a third embodiment.

FIG. 10 is a general construction diagram illustrating a vehicle airconditioning device according to a fourth embodiment.

FIG. 11 is a general construction diagram illustrating a vehicle airconditioning device according to a fifth embodiment.

FIG. 12 is an enlarged view illustrating a magnetic refrigeratoraccording to the fifth embodiment.

FIG. 13 is a general construction diagram illustrating a vehicle airconditioning device according to a sixth embodiment.

FIG. 14 is a general construction diagram illustrating a vehicle airconditioning device according to a seventh embodiment.

FIG. 15 is an enlarged view illustrating a main portion of a magneticrefrigerator according to an eighth embodiment.

FIG. 16 is an enlarged view illustrating a magnetic refrigeratoraccording to a ninth embodiment.

FIG. 17 is a section view taken along a line B-B in FIG. 16.

FIG. 18 is a section view taken along a line C-C in FIG. 16.

FIG. 19 is an enlarged view illustrating a magnetic refrigeratoraccording to a tenth embodiment.

FIG. 20 is a section view taken along a line D-D in FIG. 19.

FIG. 21 is a section view taken along a line E-E in FIG. 19.

FIG. 22 is a schematic section view illustrating a nozzle type fluiddiode according to an 11th embodiment.

FIG. 23 is an explanatory view illustrating a vortex type fluid diodeaccording to the 11th embodiment.

MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present disclosure will be described onthe basis of the drawings. In the respective embodiments to be describedbelow, parts identical or equivalent to each other are denoted by thesame reference symbols in the drawings.

First Embodiment

A first embodiment of the present disclosure will be described on thebasis of FIG. 1 to FIG. 7. FIG. 1 is a general construction diagram of avehicle air conditioning device 1 of the present embodiment. In thepresent embodiment, a magnetic refrigeration system 2 of the presentdisclosure is applied to the vehicle air conditioning device 1 forair-conditioning an interior of a passenger compartment of anautomobile.

The vehicle air conditioning device 1 of the present embodiment is anair conditioning device mounted in the automobile acquiring a driveforce for driving from an internal combustion engine (engine).

The vehicle air conditioning device 1, as shown in FIG. 1, is providedwith the magnetic refrigeration system 2 arranged in an enginecompartment, an indoor air conditioning unit 10 arranged in thepassenger compartment, and an air conditioning control device 100.

The magnetic refrigeration system 2 of the present embodiment isconstructed in such a way as to be capable of switching a refrigerantcircuit of a cooling mode for cooling the interior of the passengercompartment, a heating mode for heating the interior of the passengercompartment, and a dehumidifying mode for humidifying the interior ofthe passenger compartment at the heating time. Hence, the vehicle airconditioning device 1 can cool, heat, and dehumidify the interior of thepassenger compartment.

Specifically, the magnetic refrigeration system 2 of the presentembodiment employs an AMR (Active Magnetic Refrigeration) system ofstoring cold heat and hot heat generated by a magnetocaloric effect in amagnetic working material 30 itself. The magnetic refrigeration system 2of the present embodiment is constructed of a magnetic refrigerator 3for generating the cold heat and the hot heat by the magnetocaloriceffect, a high temperature side refrigerant circuit (first refrigerantcirculation circuit) 4 for circulating refrigerant whose temperature isincreased by the hot heat generated by the magnetic refrigerator 3 in aheating heat exchanger (first heat exchanger) 13, a low temperature siderefrigerant circuit (second refrigerant circulation circuit) 5 forcirculating the refrigerant whose temperature is decreased by the coldheat generated by the magnetic refrigerator 3 in a cooling heatexchanger (second heat exchanger) 12, and the like.

The magnetic refrigerator 3 is constructed of: a heat exchange container31 having working chambers 311 formed therein, the working chamber 311receiving the magnetic working material 30 having the magnetocaloriceffect and having refrigerant (for example, water or antifreezesolution) of a heat transporting medium flowing therethrough; a magneticfield applying and removing device 32 for applying and removing amagnetic field to and from the magnetic working material 30; arefrigerant pump 34 for transferring the refrigerant in the heatexchange container 31; an electric motor 35 corresponding to a drivesource of the magnetic refrigerator 3; and the like.

FIG. 2 is an enlarged view of the magnetic refrigerator 3, and FIG. 3 isa section view taken on a line A-A in FIG. 2. For the sake ofconvenience of description, in FIG. 2, a section in an axial directionof the magnetic refrigerator 3 is shown.

As shown in FIG. 2, the heat exchange container 31 of the presentembodiment is divided into a high temperature side container 31 a forgenerating the hot heat by the magnetocaloric effect and a lowtemperature side container 31 b for generating the cold heat by themagnetocaloric effect. The high temperature side container 31 a and thelow temperature side container 31 b are arranged side by side in acoaxial direction with the refrigerant pump 34 interposed between them.

Each of the high temperature side container 31 a and the low temperatureside container 31 b is constructed of a cylindrical container. Each ofthe containers 31 a, 31 b has the working chambers 311 formed therein,the working chamber 311 receiving the magnetic working material 30 in awall portion constructing an outer shape and having the refrigerantflowing therethrough. Here, as shown in FIG. 3, each of the containers31 a, 31 b has a plurality of working chambers 311 formed thereinradially in a circumferential direction.

Further, high temperature side and low temperature side refrigerantports 312, 313 are respectively formed in end faces of the heat exchangecontainer 31 (on sides opposite to the refrigerant pump 34 in therespective containers 31 a, 31 b), and the refrigerant can be sucked anddischarged through the refrigerant ports 312, 313.

Still further, end faces adjacent to the refrigerant pump 34 in therespective containers 31 a, 31 b have communication passages 314, 315respectively formed therein, the communication passages 314, 315communicating with the interior of the cylinder bore 344 of therefrigerant pump 34 which will be described later. In this regard, thecommunication passages 314, 315 are formed plurally in correspondence tothe respective high temperature side ports 312 and to the respective lowtemperature side ports 313.

Of the refrigerant ports 312, 313, the high temperature side ports 312formed in the high temperature side container 31 a are formed incorrespondence to the respective working chambers 311 of the hightemperature side container 31 a and communicate with the correspondingworking chambers 311.

Each of the high temperature side ports 312 is constructed of arefrigerant suction part 312 a for sucking the refrigerant and arefrigerant discharge part 312 b for discharging the refrigerant. Therefrigerant suction part 312 a is provided with a suction valve 312 copened at the time of sucking the refrigerant, and the refrigerantdischarge part 312 b is provided with a discharge valve 312 d opened atthe time of discharging the refrigerant. Each of the suction valve 312 cand the discharge valve 312 d of the present embodiment is a reed valveconstructed of an elastic plate member having one end fixed.

Still further, of the refrigerant ports 312, 313, the low temperatureside ports 313 formed in the low temperature side container 31 b areformed in correspondence to the respective working chambers 311 of thelow temperature side container 31 b and communicate with thecorresponding working chambers 311.

As is the case with the high temperature side ports 312, each of the lowtemperature side ports 313 is constructed of a refrigerant suction part313 a and a refrigerant discharge part 313 b. The refrigerant suctionpart 313 a is provided with a suction valve 313 c and the refrigerantdischarge part 313 b is provided with a discharge valve 313 d.

Still further, end faces adjacent to the refrigerant pump 34 in therespective containers 31 a, 31 b have communication passages 314, 315respectively formed therein, the communication passages 314, 315communicating with the interior of the cylinder bore 344 of therefrigerant pump 34 which will be described later. In this regard, thecommunication passages 314, 315 are formed plurally in correspondence tothe respective high temperature side ports 312 and to the respective lowtemperature side ports 313.

In the respective containers 31 a, 31 b are received rotary shafts 321a, 321 b, rotors (rotors) 322 a, 322 b fixed respectively to the rotaryshafts 321 a, 321 b, and permanent magnets 323 a, 323 b embeddedrespectively in the outer circumferential faces of the rotors 322 a, 322b, which construct parts of the magnetic field applying and removingdevice 32.

Each of the rotary shafts 321 a, 321 b is rotatably supported by supportmembers 36 a, 36 b disposed on both end portions in a longitudinaldirection of each of the containers 31 a, 31 b.

The high temperature side rotary shaft 321 a received in the hightemperature side container 31 a has an end portion, adjacent to therefrigerant pump 34, extended to the outside of the high temperatureside container 31 a and coupled to a drive shaft 341 of the refrigerantpump 34, which will be described later, via a speed change mechanism 37a which will be described later.

Further, the low temperature side rotary shaft 321 b received in the lowtemperature side container 31 b has an end portion, on the refrigerantpump 34, extended to the outside of the low temperature side container31 b and coupled to the drive shaft 341 of the refrigerant pump 34,which will be described later, via a speed change mechanism 37 b whichwill be described later. Still further, the low temperature side rotaryshaft 321 b has an end portion on the side opposite to the refrigerantpump 34 extended to the outside of the low temperature side container 31b and coupled to the electric motor 35 for rotating the respectiverotary shafts 321 a, 321 b. The electric motor 35 will be describedlater.

The rotor 322 a, 322 b is fixed to the rotary shaft 321 a, 321 b in sucha way as to rotate with a given air gap from the inner circumferentialface of the container 31 a, 31 b in a state where the rotor 322 a, 322 bhas the permanent magnet 323 a, 323 b disposed on its outercircumferential face.

Still further, as shown in FIG. 3, the permanent magnet 323 a, 323 b isdisposed on the outer circumferential face (for example, a range ofabout ¼ of the outer circumferential faces) in the rotor 322 a, 322 b insuch a way as to periodically come near to the upper working chambers311 and the lower working chambers 311 in the container 31 a, 31 baccording to the rotation of the rotary shaft 321 a, 321 b.

In this way, according to the rotation of the rotary shaft 321 a, 321 b,a magnetic field generated around the permanent magnet 323 a, 323 b isapplied to the magnetic working material 30 received on the side near tothe permanent magnet 323 a, 323 b in the container 31 a, 31 b and isremoved from the magnetic working material 30 disposed on the side farfrom the permanent magnet 323 a, 323 b in the container 31 a, 31 b.

The refrigerant pump 34 constructs a refrigerant transfer part fortransferring the refrigerant between the high temperature side ports 312and the low temperature side ports 313 which are formed in the heatexchanger container 31. In the present embodiment, a piston pump of atandem type in which two compression mechanisms are coaxially activatedby one drive shaft 341 is employed as the refrigerant pump 34.

Specifically, the refrigerant pump 34 of the present embodiment, asshown in FIG. 2, is constructed of: a housing 340; the drive shaft 341rotatably supported in the housing 340; a swash plate 342 having a slantface slanted with respect to the drive shaft 341 and rotated integrallywith the drive shaft 341; a piston 343 reciprocated according to therotation of the swash plate 342; the cylinder bore 344 formed on bothsides of the piston 343 in the housing 340; and the like.

The drive shaft 341 is rotatably supported by support members 340 a, 340b disposed on both end portions in the longitudinal direction of thehousing 340. The drive shaft 341 has both end portions thereof extendedto the outside of the housing 340 and coupled to the high temperatureside rotary shaft 321 a and the low temperature side rotary shaft 321 bvia the respective speed change mechanisms 37 a, 37 b.

Here, the respective speed change mechanisms 37 a, 37 b construct apower transmission mechanism for transmitting power generated by theelectric motor 35 to the refrigerant pump 34 via the low temperatureside rotary shaft 321 b coupled to the electric motor 35. Each of thespeed change mechanisms 37 a, 37 b of the present embodiment isconstructed in such a way as to adjust the ratio (speed reducing ratio)of the number of revolutions of each of the rotary shafts 321 a, 321 bto the number of revolutions of the drive shaft 341 of the refrigerantpump 34. The speed reducing ratio is determined according to the numberof poles of each of the permanent magnets 323 a, 323 b fixedrespectively to the rotary shafts 321 a, 321 b. For example, in the casewhere the number of poles of each of the permanent magnets 323 a, 323 bis n poles, the speed reducing ratio can be determined to be 1/n in sucha way that when the drive shaft 341 of the refrigerant pump 34 isrotated by n, each of the rotary shafts 321 a, 321 b are rotated by one.

The cylinder bore 344 is constructed of a high temperature side borepart 344 a corresponding to the respective communication passages 314 ofthe high temperature side container 31 a and a low temperature side borepart 344 b corresponding to the respective communication passages 315 ofthe low temperature side container 31 b. Here, the cylinder bore 344 isconstructed in such a way that the refrigerant in the high temperatureside bore part 344 a can exchange heat with the refrigerant in the lowtemperature side bore part 344 b.

Here, the refrigerant pump 34 of the present embodiment is constructedin such a way as to suck or discharge the refrigerant from or into therespective containers 31 a, 31 b in synchronization with applying andremoving the magnetic field to and from the magnetic working material30.

For example, the refrigerant pump 34 is constructed in the followingway: when the magnetic field is applied to the magnetic working material30 in the respective working chambers 311 disposed on the upper side ofeach of the containers 31 a, 31 b, the refrigerant pump 34 dischargesthe refrigerant in sequence into the respective working chambers 311disposed on the upper side in the high temperature side container 31 aand sucks the refrigerant in sequence from the respective workingchambers 311 disposed on the upper side in the low temperature sidecontainer 31 b. At this time, by the refrigerant pump 34, therefrigerant is sucked in sequence from the respective working chambers311 disposed on the lower side in the high temperature side container 31a and is discharged in sequence into the respective working chambers 311disposed on the lower side in the low temperature side container 31 b.

On the other hand, the refrigerant pump 34 is constructed in thefollowing way: when the magnetic field is removed from the magneticworking material 30 in the respective working chambers 311 disposed onthe upper side of each of the containers 31 a, 31 b, the refrigerantpump 34 sucks the refrigerant in sequence from the respective workingchambers 311 disposed on the upper side in the high temperature sidecontainer 31 a and discharges the refrigerant in sequence into therespective working chambers 311 disposed on the upper side in the lowtemperature side container 31 b.

When the refrigerant is discharged into the working chambers 311 of therespective containers 31 a, 31 b by the refrigerant pump 34, thedischarge valves 312 d, 313 d disposed at the refrigerant dischargeparts 312 b, 313 b of the respective containers 31 a, 31 b are opened,whereby the refrigerant near the refrigerant discharge parts 312 b, 313b in the respective containers 31 a, 31 b is discharged to the outside.

On the other hand, when the refrigerant is sucked from the workingchambers 311 of the respective containers 31 a, 31 b by the refrigerantpump 34, the suction valves 312 c, 313 d disposed at the refrigerantsuction parts 312 a, 313 a of the respective containers 31 a, 31 b areopened, whereby the refrigerant is introduced from the outside intoportions near the refrigerant suction parts 312 a, 313 a in therespective containers 31 a, 31 b.

In this way, in the magnetic refrigerator 3, the refrigerant can besucked or discharged in sequence from or into the respective workingchambers 311 in the respective containers 31 a, 31 b in synchronizationwith applying and removing the magnetic field to and from the magneticworking material 30, so that the refrigerant near the refrigerantdischarge parts 312 b, 313 b in the respective containers 31 a, 31 b canbe continuously discharged to the outside.

Returning to FIG. 1, the electric motor 35 is a drive part that isactivated by electric power supplied from a battery (not shown) mountedin the automobile and that supplies power to the rotary shafts 321 a,321 b and the drive shaft 341 to thereby drive the magnetic refrigerator3.

Here, in the present embodiment, the rotary shafts 321 a, 321 b, therotors 322 a, 322 b, the permanent magnets 323 a, 323 b, which arereceived respectively in the containers 31, 31 b, and the electric motor35 disposed on the outside of the heat exchange container 31 constructthe magnetic field applying and removing device 32 that is a magneticfield applying and removing part. Further, each of the permanent magnets323 a, 323 b constructs a magnetic field generating part for generatinga magnetic field.

Next, the high temperature side refrigerant circuit 4 and the lowtemperature side refrigerant circuit 5 will be described. First,describing the high temperature side refrigerant circuit 4, the hightemperature side refrigerant circuit 4 is a refrigerant circulationcircuit for introducing the refrigerant discharged from the refrigerantdischarge parts 312 b of the high temperature side ports 312 in the hightemperature side container 31 a into a refrigerant flow-in port 13 a ofthe heating heat exchanger 13 and for returning the refrigerant flowingout of a refrigerant flow-out port 13 b of the heating heat exchanger 13into the refrigerant suction parts 312 a of the high temperature sideports 312.

Specifically, the refrigerant discharge parts 312 b of the hightemperature side ports 312 have the refrigerant flow-in port 13 a of theheating heat exchanger 13 connected thereto. The heating heat exchanger13 is a heat exchanger (first heat exchanger) that is arranged in a case11 of the indoor air conditioning unit 10 to be described later and thatmakes the refrigerant flowing through the case 11 exchange heat withblown air after passing through the cooling heat exchanger 12 to bedescribed later to thereby heat the blown air.

The refrigerant flow-out port 13 b of the heating heat exchanger 13 hasa first electric three-way valve 41 connected thereto. The firstelectric three-way valve 41 constructs a flow passage switching partwhose activation is controlled by a control signal outputted from theair conditioning control device 100.

More specifically, the first electric three-way valve 41 switches arefrigerant circuit for connecting the refrigerant flow-out port 13 b ofthe heating heat exchanger 13 to the refrigerant suction part 312 a ofthe high temperature side container 31 a and a refrigerant flow passagefor connecting the refrigerant flow-out port 13 b of the heating heatexchanger 13 to a heat radiation side refrigerant flow-in port 61 a of aheat absorbing and radiating heat exchanger 6.

The heat absorbing and radiating heat exchanger 6 is an outdoor heatexchanger that is arranged in the engine compartment and that makes therefrigerant flowing through itself exchange heat with an outside air.The heat absorbing and radiating heat exchanger 6 of the presentembodiment is constructed of two heat exchange parts corresponding to aheat radiating part 61 through which the refrigerant flowing out of theheating heat exchanger 13 flows and a heat absorption part 62 throughwhich the refrigerant discharged from the low temperature side container31 b flows.

The heat radiating part 61 of the heat absorbing and radiating heatexchanger 6 is a heat exchange part for making the refrigerantflowing-in (refrigerant flowing out of the heating heat exchanger 13)through the heat radiation side refrigerant flow-in port 61 a exchangeheat with the outside air. Further, the heat absorption part 62 of theheat absorbing and radiating heat exchanger 6 is a heat exchange partfor making the refrigerant flowing-in (refrigerant discharged from thelow temperature side container 31 b) through the heat absorption siderefrigerant flow-in port 62 a exchange heat with the outside air.

In this regard, the heat radiating part 61 and the heat absorption part62 have their refrigerant flow passages constructed independently ofeach other so as to prevent the refrigerant flowing through the heatradiating part 61 and the refrigerant flowing in the heat absorptionpart 62 from being mixed with each other in the heat absorbing andradiating heat exchanger 6.

The heat radiation side refrigerant flow-out port 61 b of the heatabsorbing and radiating heat exchanger 6 has the refrigerant suctionparts 312 a of the high temperature side container 31 a connectedthereto, and the refrigerant having heat radiated in the heat absorbingand radiating heat exchanger 6 is returned to the working chambers 311of the high temperature side container 31 a.

Thus, the high temperature side refrigerant circuit 4 is constructed of:a circulation circuit in which the refrigerant is circulated in order ofthe refrigerant discharge part 312 b of the high temperature sidecontainer 31 a, the heating heat exchanger 13, the first electricthree-way valve 41, and the refrigerant suction part 312 a of the hightemperature side container 31 a; and a circulation circuit in which therefrigerant is circulated in order of the refrigerant discharge part 312b of the high temperature side container 31 a, the heating heatexchanger 13, the first electric three-way valve 41, the heat radiatingpart 61 of the heat absorbing and radiating heat exchanger 6, and therefrigerant suction part 312 a of the high temperature side container 31a.

In this regard, the high temperature side refrigerant circuit 4 has areservoir tank 43 connected between the heating heat exchanger 13 andthe first electric three-way valve 41 via a fixed throttle 42, thereservoir tank 43 adjusting the amount of the refrigerant flowingthrough the high temperature side refrigerant circuit 4. As the fixedthrottle 42 can be employed an orifice or a capillary tube.

Further, the low temperature side refrigerant circuit 5 is a refrigerantcirculation circuit that introduces the refrigerant discharged from therefrigerant discharge parts 313 b of the low temperature side ports 313in the low temperature side container 31 b into the refrigerant flow-inport 12 a of the cooling heat exchanger 12 and that returns therefrigerant flowing out of the refrigerant flow-out port 12 b of thecooling heat exchanger 12 to the refrigerant suction parts 313 a of thelow temperature side ports 313.

Specifically, the refrigerant discharge parts 313 b of the lowtemperature side ports 313 have a second electric three-way valve 51connected thereto. As is the case with the first electric three-wayvalve 41, the second electric three-way valve 51 constructs a flowpassage switching part whose activation is controlled by a controlsignal outputted from the air conditioning control device 100.

The second electric three-way valve 51 switches a refrigerant circuitfor connecting the refrigerant discharge parts 313 b of the lowtemperature side ports 313 to the heat absorption side refrigerantflow-in port 62 a of the heat absorbing and radiating heat exchanger 6and a refrigerant circuit for connecting the refrigerant discharge parts313 b of the low temperature side ports 313 to a third electricthree-way valve 52 in accordance with a control signal outputted fromthe air conditioning control device 100. The heat absorption siderefrigerant flow-out port 62 b of the heat absorbing and radiating heatexchanger 6 has the third electric three-way valve 52 connected thereto.

As are the cases with the first and the second electric three-way valves41, 51, the third electric three-way valve 52 constructs a flow passageswitching part whose activation is controlled by a control signaloutputted from the air conditioning control device 100.

Specifically, the third electric three-way valve 52 is constructed insuch a way as to be activated in conjunction with the second electricthree-way valve 51. That is, when the refrigerant circuit is switched bythe second electric three-way valve 51 to a refrigerant circuit forconnecting the refrigerant discharge parts 313 b of the low temperatureside ports 313 to the third electric three-way valve 52, the thirdelectric three-way valve 52 switches the refrigerant circuit to arefrigerant circuit for connecting the second electric three-way valve51 to the refrigerant flow-in port 12 a of the cooling heat exchanger12. Further, when the refrigerant circuit is switched by the secondelectric three-way valve 51 to a refrigerant circuit for connecting therefrigerant discharge parts 313 b of the low temperature side ports 313to the heat absorption side refrigerant flow-in port 62 a of the heatabsorbing and radiating heat exchanger 6, the third electric three-wayvalve 52 switches the refrigerant circuit to a refrigerant circuit forconnecting the second electric three-way valve 51 to the refrigerantsuction parts 313 a of the low temperature side ports 313.

The cooling heat exchanger 12 connected to the third electric three-wayvalve 52 is a heat exchanger that is arranged on the upstream of theheating heat exchanger 13 in the flow of the blown air in the case 11 ofthe indoor air conditioning unit 10 and that makes the refrigerantflowing through itself exchange heat with the blown air to thereby coolthe blown air. The refrigerant suction parts 313 a of the lowtemperature side ports 313 are connected to the refrigerant flow-outport 12 b of the cooling heat exchanger 12.

In this way, the low temperature side refrigerant circuit 5 isconstructed of: a circulation circuit in which the refrigerant iscirculated in order of the refrigerant discharge parts 313 b of the lowtemperature side container 31 b, the second electric three-way valve 51,the third electric three-way valve 52, the cooling heat exchanger 12,and the refrigerant suction parts 313 a of the low temperature sidecontainer 31 b; and a circulation circuit in which the refrigerant iscirculated in order of the refrigerant discharge parts 313 b of the lowtemperature side container 31 b, the heat absorption part 62 of the heatabsorbing and radiating heat exchanger 6, the second electric three-wayvalve 51, the third electric three-way valve 52, and the refrigerantsuction parts 313 a of the low temperature side container 31 b.

In this regard, the low temperature side refrigerant circuit 5 has areservoir tank 54 connected between the second electric three-way valve51 and the heat absorbing and radiating heat exchanger 6, and the thirdelectric three-way valve 52 via a fixed throttle 53, the reservoir tank54 adjusting the amount of the refrigerant flowing through the lowtemperature side refrigerant circuit 5. As the fixed throttle 53 can beemployed an orifice or a capillary tube.

Next, the indoor air conditioning unit 10 will be described. The indoorair conditioning unit 10 is a unit that is arranged inside a meter board(instrument panel) at a forefront portion in the passenger compartmentand that receives a blower (not shown), the cooling heat exchanger 12,the heating heat exchanger 13, and a heater core 14 in the case 11 offorming the outer shape thereof.

The case 11 forms an air flow passage for the blown air to be blown intothe passenger compartment and is formed of resin having a certain degreeof elasticity and excellent in strength (for example, polypropylene). Aninside and outside air switching box (not shown) for switching andintroducing an inside air (air inside the passenger compartment) and anoutside air (air outside the passenger compartment) is arranged on themost upstream side of the flow of the blown air in the case 11.

More specifically, in the inside and outside air switching box areformed an inside air introduction port through which the inside air isintroduced into the case 11 and an outside air introduction port throughwhich the outside air is introduced into the case 11. Further, in theinside and outside air switching box is arranged an inside and outsideair switching door for continuously adjusting an opening area of theinside air introduction port and an opening area of the outside airintroduction port to thereby change a ratio of the volume of the insideair and the volume of the outside air. The inside and outside airswitching door constructs an air volume ratio changing part forswitching a suction port mode of changing the ratio of the volume of theinside air and the volume of the outside air which are introduced intothe case 11.

On the downstream side of the inside and outside air switching box inthe air flow is arranged a blower for blowing the air sucked through theinside and outside air switching box into the passenger compartment. Theblower is an electric blower for driving a centrifugal multi-blade fan(sirocco fan) by an electric motor and has the number of revolutions(the volume of blown air) controlled by a control voltage outputted fromthe air conditioning control device 100.

The cooling heat exchanger 12 is arranged on the downstream side of theblower in the air flow. On the downstream side of the cooling heatexchanger 12 in the air flow are formed air passages such as a heatingcold air passage 15 and a cold air bypass passage 16 through which theair after passing through the cooling heat exchanger 12 flows, and anair mixing space 17 in which the air flowing out of the heating cold airpassage 15 is mixed with the air flowing out of the cold air bypasspassage 16.

In the heating cold air passage 15, the heating heat exchanger 13 and aheater core 14 are arranged in this order in a direction in which theblown air flows as a heating part for heating the air after passingthrough the cooling heat exchanger 12. The heater core 14 is a heatexchanger for making cooling water of an engine (not shown) whichoutputs a drive force for running the automobile exchange heat with theair after passing through the cooling heat exchanger 12 to thereby heatthe air after passing through the cooling heat exchanger 12.

On the other hand, the cold air bypass passage 16 is an air passage forintroducing the air after passing through the cooling heat exchanger 12into the air mixing space 17 without passing through the heating heatexchanger 13 and the heater core 14. Hence, the temperature of the blownair mixed in the air mixing space 17 is changed according to the ratioof the volume of the air passing through the heating heat exchanger 15and the volume of the air passing through the cold air bypass passage16.

Thus, in the present embodiment, an air mixing door 18 for continuouslychanging the ratio of the volume of the air flowing into the heatingcold air passage 15 and the volume of the air flowing into the cold airbypass passage 16 is disposed on the downstream side of the cooling heatexchanger 12 in the air flow and on the entry side of the heating coldair passage 15 and the cold air bypass passage 16. In other words, theair mixing door 18 constructs a temperature adjusting part for adjustingthe volume of the blown air flowing into the heating heat exchanger 13to thereby adjust an air temperature in the air mixing space 17(temperature of the air blown off into the passenger compartment).

Further, on the most downstream side in the flow of the blown air in thecase 11 are arranged blowoff ports (not shown, for example, face blowoffport, foot blowoff port, and defroster blowoff port) for blowing off theblown air having temperature adjusted into the passenger compartment,which is a space to be cooled, from the air mixing space 17. In thisregard, on the upstream side of each of the blowoff ports in the airflow is arranged a door for adjusting an opening area of the blowoffport, and the blowoff ports for blowing off the conditioned air into thepassenger compartment can be switched by opening or closing therespective doors.

Next, an electric control part of the present embodiment will bedescribed. The air conditioning control device 100 is constructed of awell known microcomputer, which includes a CPU, a ROM, and a RAM, and aperipheral circuit thereof. The air conditioning control device 100performs various operations and processings on the basis of controlprograms stored in the ROM to thereby control the activations of theelectric motor 35, the respective electric three-way valves 41, 51, 52for constructing flow passage switching parts, the blower, and the drivepart of the air mixing door 18 connected to the output side.

An operation signal is inputted to the input side of the airconditioning control device 100 from various air conditioning operationswitches disposed in an operation panel (not shown) arranged near theinstrument panel in the front portion of the passenger compartment.Specifically, the various air conditioning operation switches disposedin the operation panel include an activating switch, an automaticswitch, and a selector switch of an operation mode (cooling mode,heating mode, dehumidifying mode) of the vehicle air conditioning device1.

In this regard, the air conditioning control device 100 has an electricmotor control part controlling the electric motor 35 corresponding tothe drive part of the magnetic refrigerator 3 and a flow passageswitching control part controlling the respective electric three-wayvalves 41, 51, 52.

Next, the operation of the vehicle air conditioning device 1 includingthe magnetic refrigeration system 2 of the present embodiment in theconstruction described above will be described. First, an operationprinciple of the magnetic refrigerator 3 in the magnetic refrigerationsystem 2 will be generally described on the basis of FIG. 4.

FIG. 4 illustrates enlarged views of a portion B shown in FIG. 1. Here,(a) of FIG. 4 shows a magnetic field applying process of applying amagnetic field to the magnetic working material 30, (b) of FIG. 4 showsa refrigerant discharging process of discharging the refrigerant fromthe working chamber 311, (c) of FIG. 4 shows a magnetic field removingprocess of removing the magnetic field from the magnetic workingmaterial 30, and (d) of FIG. 4 shows a refrigerant sucking process ofsucking the refrigerant into the working chamber 311.

As shown in (a) of FIG. 4, when the piston 343 in the high temperatureside bore part 344 a in the refrigerant pump 34 is positioned near abottom dead center and the permanent magnet 323 a comes near to theupper working chambers 311 of the high temperature side container 31 a,a magnetic field is applied to the magnetic working material 30 receivedin the upper working chambers 311 (that is, the magnetic workingmaterial 30 is magnetized, the magnetic field applying process). At thistime, the magnetic working material 30 generates heat by themagnetocaloric effect, whereby the refrigerant in the upper workingchambers 311 is increased in temperature.

Then, as shown in (b) of FIG. 4, the piston 343 in the high temperatureside bore part 344 a is moved from the bottom dead center to a top deadcenter and the refrigerant in the upper working chambers 311 istransferred from the refrigerant pump 34 to the high temperature sideports 312. At this time, the discharge valves 312 d disposed at therefrigerant discharge parts 312 b of the high temperature side ports 312are opened and hence the high temperature refrigerant near therefrigerant discharge parts 312 b is discharged to the heating heatexchanger 13 (refrigerant discharging process).

Then, as shown in (c) of FIG. 4, when the piston 343 in the hightemperature side bore part 344 a is positioned near the top dead centerand the permanent magnet 323 a is moved away from the upper workingchambers 311 of the high temperature side container 31 a, the magneticfield is removed from the magnetic working material 30 received in theupper working chambers 311 (that is, the magnetic working material 30 isdemagnetized, magnetic field removing process).

Then, as shown in (d) of FIG. 4, the piston 343 in the high temperatureside bore part 344 a is moved from the top dead center to the bottomdead center and the refrigerant in the upper working chambers 311 istransferred from the high temperature side ports 312 to the refrigerantpump 34. At this time, the suction valves 312 c disposed at therefrigerant suction parts 312 a of the high temperature side ports 312are opened and the refrigerant flowing out of the heating heat exchanger13 is sucked into portions near the refrigerant suction parts 312 a(refrigerant sucking process). Then, when the piston 343 of therefrigerant pump 34 is returned near the bottom dead center, there isbrought about the magnetic field applying process shown in (a) of FIG.4.

In this way, the hot heat generated by the magnetocaloric effect of themagnetic working material 30 received in the upper working chambers 311of the high temperature side container 31 a can be transported to theheating heat exchanger 13 by these four processes of the magnetic fieldapplying process, the refrigerant discharging process, the magneticfield removing process, and the refrigerant sucking process.

Here, on the lower working chambers 311 of the high temperature sidecontainer 31 a, as is the case with the upper working chambers 311, thefour processes of the magnetic field applying process, the refrigerantdischarging process, the magnetic field removing process, and therefrigerant sucking process are performed, which is different only intiming from the processes performed on the upper working chambers 311.

Here, although not shown, on the upper working chambers 311 of the lowtemperature side container 31 b, at the time of the magnetic fieldapplying process on the upper working chambers 311 of the hightemperature side container 31 a, the magnetic field is applied to themagnetic working material 30 in a state where the piston 343 in the lowtemperature side bore part 344 b is positioned near the top dead center.

Then, the piston 343 in the low temperature side bore part 344 b ismoved from the top dead center to the bottom dead center and therefrigerant in the upper working chambers 311 is transferred from thelow temperature side ports 313 to the refrigerant pump 34. At this time,the suction valves 313 c disposed at the refrigerant suction parts 313 aof the low temperature side ports 313 are opened and the refrigerantflowing out of the cooling heat exchanger 12 is sucked into portionsnear the refrigerant suction parts 313 a (refrigerant sucking process).

Then, on the upper working chambers 311 of the low temperature sidecontainer 31 b, at the time of the magnetic field removing process onthe upper working chambers 311 of the high temperature side container 31a, the magnetic field is removed from the magnetic working material 30received in the upper working chambers 311 in a state where the piston343 in the low temperature side bore part 344 b is positioned near thebottom dead center.

Then, the piston 343 in the low temperature side bore part 344 b ismoved from the bottom dead center to the top dead center and therefrigerant in the upper working chambers 311 is transferred from therefrigerant pump 34 to the low temperature side ports 313. At this time,the discharge valves 313 d disposed at the refrigerant discharge parts313 b of the low temperature side ports 313 are opened and therefrigerant near the refrigerant discharge parts 312 b is discharged tothe cooling heat exchanger 12 side (refrigerant discharging process).

In this way, the cold heat generated by the magnetocaloric effect of themagnetic working material 30 received in the upper working chambers 311of the low temperature side container 31 b can be transported to thecooling heat exchanger 12 by these four processes of the magnetic fieldapplying process, the refrigerant discharging process, the magneticfield removing process, and the refrigerant sucking process.

In this regard, on the lower working chambers 311 of the low temperatureside container 31 b, as is the case with the upper working chambers 311,the four processes of the magnetic field applying process, therefrigerant discharging process, the magnetic field removing process,and the refrigerant sucking process are performed, which is differentonly in timing from the processes performed on the upper workingchambers 311.

Here, when the heat exchange container 31 is viewed on the whole, afterthe magnetic field is applied to the magnetic working material 30, therefrigerant is transferred from the low temperature side ports 313 tothe high temperature side ports 312, whereas after the magnetic field isremoved from the magnetic working material 30, the refrigerant istransferred from the high temperature side ports 312 to the lowtemperature side ports 313.

Then, the magnetic field applying process, the refrigerant dischargingprocess, the magnetic field removing process, and the refrigerantsucking process are repeated on the high temperature side container 31 ain the heat exchange container 31, and the magnetic field applyingprocess, the refrigerant discharging process, the magnetic fieldremoving process, and the refrigerant sucking process are repeated onthe low temperature side container 31 b, whereby a large temperaturegradient can be generated between the magnetic working material 30received in the upper working chambers 311 of the high temperature sidecontainer 31 a and the magnetic working material 30 received in theupper working chambers 311 of the low temperature side container 31 b.

Next, an action at the time of each operation mode of the vehicle airconditioning device 1 will be described on the basis of FIG. 5 to FIG.7. Each operation mode is set as appropriate by a selector switch of theoperation mode disposed in the operation panel or by a controlprocessing of the air conditioning control device 100. Here, FIG. 5shows the refrigerant circuit at the time of the cooling mode, FIG. 6shows the refrigerant circuit at the time of the heating mode, and FIG.7 shows the refrigerant circuit at the time of the dehumidifying mode.

(A) Cooling Mode (see FIG. 5)

In the cooling mode, the high temperature side refrigerant circuit 4 isswitched to the refrigerant circuit for connecting the refrigerantflow-out port 13 b of the heating heat exchanger 13 to the heatradiation side refrigerant flow-in port 61 a of the heat absorbing andradiating heat exchanger 6 by the first electric three-way valve 41according to a control signal from the air conditioning control device100. Further, the low temperature side refrigerant circuit 5 is switchedby the second electric three-way valve 51 to the refrigerant circuit forconnecting the refrigerant discharge parts 313 b of the low temperatureside ports 313 to the third electric three-way valve 52 and is switchedby the third electric three-way valve 52 to the refrigerant circuit forconnecting the second electric three-way valve 51 to the refrigerantflow-in port 12 a of the cooling heat exchanger 12.

In this way, as shown by arrows in FIG. 5, in the high temperature siderefrigerant circuit 4 is constructed a circulation circuit in which therefrigerant is circulated in order of the magnetic refrigerator 3, theheating heat exchanger 13, the first electric three-way valve 41, theheat radiating part 61 of the heat absorbing and radiating heatexchanger 6, and the magnetic refrigerator 3. Further, in the lowtemperature side refrigerant circuit 5 is constructed a circulationcircuit in which the refrigerant is circulated in order of the magneticrefrigerator 3, the second electric three-way valve 51, the thirdelectric three-way valve 52, the cooling heat exchanger 12, and themagnetic refrigerator 3.

Thus, the refrigerant having temperature increased by the magneticrefrigerator 3 is discharged from the refrigerant discharge parts 312 bof the high temperature side container 31 a of the magnetic refrigerator3 to the heating heat exchanger 13 and exchanges heat with the blown air(cold air) after passing through the cooling heat exchanger 12 in theheating heat exchanger 13, thereby being cooled. The refrigerant flowingout of the heating heat exchanger 13 exchanges heat with the outside airin the heat radiating part 61 of the heat absorbing and radiating heatexchanger 6, thereby being cooled. Then, the refrigerant is sucked intothe high temperature side container 31 a via the refrigerant suctionparts 312 a of the magnetic refrigerator 3, thereby being againincreased in temperature.

On the other hand, the refrigerant having temperature decreased by themagnetic refrigerator 3 is discharged from the low temperature sideports 313 of the low temperature side container 31 b of the magneticrefrigerator 3 to the cooling heat exchanger 12 and absorbs heat fromthe blown air in the cooling heat exchanger 12. In this way, the blownair passing through the cooling heat exchanger 12 is cooled.

At this time, the opening of the air mixing door 18 in the case 11 isadjusted, whereby a portion (or all) of the blown air cooled by thecooling heat exchanger 12 flows into the cold air bypass passage 16 andthen flows into the air mixing space 17, whereas a portion (or all) ofthe blown air cooled by the cooling heat exchanger 12 flows into theheating cold air passage 15 and is again heated at the time of passingthrough the heating heat exchanger 13 and the heater core 14 and thenflows into the air mixing space 17.

In this way, both portions of the blown air are mixed in the air mixingspace 17 and hence the temperature of the blown air to be blown off intothe passenger compartment is adjusted to a desired temperature, wherebythe interior of the passenger compartment can be cooled. In the coolingmode, the blown air has also a high dehumidifying capacity but hardlyexerts a heating capacity.

Here, the refrigerant flowing out of the cooling heat exchanger 12 issucked into the low temperature side container 31 b via the refrigerantsuction parts 313 a of the magnetic refrigerator 3, thereby being againdecreased in temperature.

(B) Heating Mode (see FIG. 6)

In the heating mode, the high temperature side refrigerant circuit 4 isswitched to the refrigerant circuit for connecting the refrigerantflow-out port 13 b of the heating heat exchanger 13 to the refrigerantsuction parts 312 a of the high temperature side container 31 a by thefirst electric three-way valve 41 according to a control signal from theair conditioning control device 100. Further, the low temperature siderefrigerant circuit 5 is switched to the refrigerant circuit forconnecting the refrigerant discharge parts 313 b of the low temperatureside ports 313 to the heat absorption side refrigerant flow-in port 62 aof the heat absorbing and radiating heat exchanger 6 by the secondelectric three-way valve 51 and is switched to the refrigerant circuitfor connecting the second electric three-way valve 51 to the refrigerantsuction parts 313 a of the low temperature side ports 313 by the thirdelectric three-way valve 52.

In this way, as shown by arrows in FIG. 6, in the high temperature siderefrigerant circuit 4 is constructed a circulation circuit in which therefrigerant is circulated in order of the magnetic refrigerator 3, theheating heat exchanger 13, the first electric three-way valve 41, andthe magnetic refrigerator 3. Further, in the low temperature siderefrigerant circuit 5 is constructed a circulation circuit in which therefrigerant is circulated in order of the magnetic refrigerator 3, theheat absorption part 62 of the heat absorbing and radiating heatexchanger 6, the second electric three-way valve 51, the third electricthree-way valve 52, and the magnetic refrigerator 3.

Thus, the refrigerant having temperature increased by the magneticrefrigerator 3 is discharged from the refrigerant discharge parts 312 bof the high temperature side container 31 a of the magnetic refrigerator3 to the heating heat exchanger 13 and exchanges heat with the blown airblown from the blower in the heating heat exchanger 13, thereby beingcooled. In this way, the blown air passing through the heating heatexchanger 13 is heated.

At this time, since the opening of the air mixing door 18 is adjusted,as is the case with the cooling mode, both portions of the blown air aremixed in the air mixing space 17 and the temperature of the blown airblown off into the passenger compartment can be adjusted to a desiredtemperature and the interior of the passenger compartment can be heated.Here, in the heating mode, the dehumidifying capacity of the blown airis not exerted.

The refrigerant flowing out of the heating heat exchanger 13 is suckedinto the high temperature side container 31 a via the refrigerantsuction parts 312 a of the magnetic refrigerator 3, thereby being againincreased in temperature.

On the other hand, the refrigerant having temperature decreased by themagnetic refrigerator 3 is discharged from the low temperature sideports 313 of the low temperature side container 31 b of the magneticrefrigerator 3 to the heat absorbing and radiating heat exchanger 6 andexchanges heat with the outside air in the heat absorption part 62 ofthe heat absorbing and radiating heat exchanger 6, thereby beingincreased in temperature. The refrigerant flowing out of the heatabsorption part 62 of the heat absorbing and radiating heat exchanger 6is sucked into the low temperature side container 31 b via therefrigerant suction parts 313 a of the magnetic refrigerator 3, therebybeing again decreased in temperature.

(C) Dehumidifying Mode (see FIG. 7)

In the dehumidifying mode, the high temperature side refrigerant circuit4 is switched to the refrigerant circuit for connecting the refrigerantflow-out port 13 b of the heating heat exchanger 13 to the refrigerantsuction parts 312 a of the high temperature side container 31 a by thefirst electric three-way valve 41 according to a control signal from theair conditioning control device 100. Further, the low temperature siderefrigerant circuit 5 is switched to the refrigerant circuit forconnecting the refrigerant discharge parts 313 b of the low temperatureside ports 313 to the third electric three-way valve 52 by the secondelectric three-way valve 51 and is switched to the refrigerant circuitfor connecting the second electric three-way valve 51 to the refrigerantflow-in port 12 a of the cooling heat exchanger 12 by the third electricthree-way valve 52.

In this way, as shown by arrows in FIG. 7, in the high temperature siderefrigerant circuit 4 is constructed a circulation circuit in which therefrigerant is circulated in order of the magnetic refrigerator 3, theheating heat exchanger 13, the first electric three-way valve 41, andthe magnetic refrigerator 3. Further, in the low temperature siderefrigerant circuit 5 is constructed a circulation circuit in which therefrigerant is circulated in order of the magnetic refrigerator 3, thesecond electric three-way valve 51, the third electric three-way valve52, the cooling heat exchanger 12, and the magnetic refrigerator 3.

Thus, the refrigerant having temperature increased by the magneticrefrigerator 3 is discharged from the refrigerant discharge parts 312 bof the high temperature side container 31 a of the magnetic refrigerator3 to the heating heat exchanger 13 and exchanges heat with the blown air(cold air) after passing through the cooling heat exchanger 12 in theheating heat exchanger 13, thereby being cooled. In this way, the blownair passing through the heating heat exchanger 13 is heated.

On the other hand, the refrigerant having temperature decreased by themagnetic refrigerator 3 is discharged from the low temperature sideports 313 of the low temperature side container 31 b of the magneticrefrigerator 3 to the cooling heat exchanger 12 and absorbs heat fromthe blown air in the cooling heat exchanger 12. In this way, the blownair passing through the cooling heat exchanger 12 is cooled anddehumidified.

In this way, the blown air cooled and dehumidified by the cooling heatexchanger 12 is again heated at the time of passing through the heatingheat exchanger 13 and the heater core 14 and is blown off into thepassenger compartment from the air mixing space 17. In other words, theinterior of the passenger compartment can be dehumidified. Here, in thedehumidifying mode, the humidifying capacity of the blown air can beexerted but the heating capacity is reduced as compared with the heatingmode.

The refrigerant flowing out of the heating heat exchanger 13 is suckedinto the high temperature side container 31 a via the refrigerantsuction parts 312 a of the magnetic refrigerator 3, thereby being againincreased in temperature.

The vehicle air conditioning device 1 including the magneticrefrigeration system 2 of the present embodiment is activated in themanner described above and hence can produce the following excellentadvantages.

As described above, in the working chambers 311 of the heat exchangecontainer 31 in the magnetic refrigerator 3, the magnetic field isapplied to the magnetic working material 30 and then the refrigerant istransferred from the low temperature side ports 313 to the hightemperature side ports 312, whereby the refrigerant near the hightemperature side ports 312, whose temperature is increased by the hotheat of the magnetic working material 30 caused by applying the magneticfield, can be made to flow into the heating heat exchanger 13 via thehigh temperature side refrigerant circuit 4.

Further, in the working chambers 311 of the heat exchange container 31in the magnetic refrigerator 3, the magnetic field is removed from themagnetic working material 30 and then the refrigerant is transferredfrom the high temperature side ports 312 to the low temperature sideports 313, whereby the refrigerant near the low temperature side ports313, whose temperature is decreased by the cold heat of the magneticworking material 30 caused by removing the magnetic field, can be madeto flow into the cooling heat exchanger 12 via the low temperature siderefrigerant circuit 5.

In this way, the refrigerant having temperature increased by the hotheat generated in the magnetic working material 30 can be made todirectly flow into the heating heat exchanger 13 and the refrigeranthaving temperature decreased by the cold heat generated in the magneticworking material 30 can be made to directly flow into the cooling heatexchanger 12. As a result, a heat exchange loss can be reduced when thehot heat and the cold heat generated in the magnetic working material 30are transported to the respective heat exchangers 12, 13.

For example, a temperature of refrigerant at the high temperature sideports 312 of the heat exchange container 31 in the magnetic refrigerator3 is defined as Th, and a temperature of refrigerant at the lowtemperature side ports 313 is defined as Tl (<Th). Further, a cycleefficiency η of the magnetic refrigeration system 2 is defined as 80% ofa cycle efficiency ηth of an ideal Carnot cycle. At this time, in aconstruction in which the hot heat and the cold heat of the refrigerantin the heat exchange container 31 are transported directly to theheating heat exchanger 13 and the cooling heat exchanger 12, as in thepresent embodiment, COP can be expressed by the following mathematicalformula F1.

COP={Th/(Th−Tl)}×80/100  (F1)

On the other hand, in a construction in which the hot heat and the coldheat of the refrigerant in the heat exchange container 31 aretransported indirectly to the heating heat exchanger 13 and the coolingheat exchanger 12, as in the prior art, temperatures on the heating heatexchanger 13 and the cooling heat exchanger 12 become temperatures(Th−ΔT, Tl−ΔT) acquired by subtracting a heat exchange loss ΔT from Th,Tl, then COP can be expressed by the following mathematical formula F2.

COP={(Th−ΔT)/(Th−Tl)}×80/100  (F2)

In this way, in the magnetic refrigeration system 2 of the presentembodiment, the heat exchange loss ΔT can be reduced when the hot heatand the cold heat generated in the magnetic working material 30 aretransported to the respective heat exchangers 12, 13. Hence, as comparedwith the magnetic refrigeration system of the prior art, the COP of themagnetic refrigeration system 2 can be improved.

The magnetic refrigerator 3 employing the AMR system has a constructionin which the refrigerant in the working chambers 311 of the heatexchange container 31 is transferred between the high temperature sideports 312 and the low temperature side ports 313. For this reason, if itis employed a construction in which the ports 312, 313 of the heatexchange container 31 are connected to the corresponding heat exchanger12, 13 simply by the use of piping or the like, the refrigerantdischarged from the respective ports 312, 313 toward the heat exchanger12, 13 is likely to be sucked into the working chambers 311 of the heatexchange container 31 before the refrigerant flows into the heatexchanger 12, 13.

In this case, the heat of the refrigerant discharged from each of theports 312, 313 toward each of the heat exchangers 12, 13 is onlytransmitted to the refrigerant in each of the heat exchangers 12, 13 viathe refrigerant in the piping and a long time is required to make thetemperature of the refrigerant in each of the heat exchangers 12, 13 tohave a desired temperature.

In contrast to this, in the present embodiment, the high temperatureside ports 312 of the heat exchange container 31 is connected to theheating heat exchanger 13 by the high temperature side refrigerantcircuit 4 constructed in such a way that the refrigerant discharged fromthe high temperature side ports 312 passes through the heating heatexchanger 13 and again returns to the high temperature side ports 312,so that the refrigerant discharged from the high temperature side ports312 of the heat exchange container 31 can be made to flow into theheating heat exchanger 13.

Similarly, the low temperature side ports 313 of the heat exchangecontainer 31 is connected to the cooling heat exchanger 12 by the lowtemperature side refrigerant circuit 5 constructed in such a way thatthe refrigerant discharged from the low temperature side ports 313passes through the cooling heat exchanger 12 and again returns to thelow temperature side ports 313, so that the refrigerant discharged fromthe low temperature side ports 313 of the heat exchange container 31 canbe made to flow into the cooling heat exchanger 12.

Further, the present embodiment employs a construction in which each ofthe ports 312, 313 of the heat exchange container 31 is provided withthe suction valve opened when the refrigerant is sucked into the workingchambers 311 of the heat exchange container 31 and the discharge valveopened when the refrigerant is discharged from the working chambers 311of the heat exchange container 31.

For this reason, after the magnetic field is applied to the magneticworking material 30, the refrigerant near the high temperature sideports 312, whose temperature is increased by the hot heat generated inthe magnetic working material 30 by applying the magnetic field, can bemade to surely flow into the heating heat exchanger 13 and therefrigerant flowing out of the heating heat exchanger 13 can be suckedinto the working chambers 311 of the heat exchange container 31.

Similarly, after the magnetic field is removed from the magnetic workingmaterial 30, the refrigerant near the low temperature side ports 313,whose temperature is decreased by the cold heat generated in themagnetic working material 30 by removing the magnetic field can be madeto surely flow into the cooling heat exchanger 12 and the refrigerantflowing out of the cooling heat exchanger 12 can be sucked into theworking chambers 311 of the heat exchange container 31.

Further, the present embodiment employs the construction in which therotary shafts 321 a, 321 b of the magnetic field applying and removingdevice 32 are coupled to the drive shaft 341 of the refrigerant pump 34and in which the refrigerant pump 34 is driven by the electric motor 35which is the drive part of the magnetic field applying and removingdevice 32.

According to this construction, the drive source of the magnetic fieldapplying and removing device 32 can be made common to the drive sourceof the refrigerant pump 34, so that the magnetic refrigeration system 2can be realized by a simple construction. Accordingly, the powerconsumption in the magnetic refrigeration system 2 can be restrictedfrom increasing, and the COP of the magnetic refrigeration system 2 canbe further improved.

Second Embodiment

Next, a second embodiment of the present disclosure will be described onthe basis of FIG. 8. FIG. 8 is a general construction diagram of avehicle air conditioning device 1 of the present embodiment. In thepresent embodiment, the descriptions of parts identical or equivalent tothe parts in the first embodiment will be omitted or simplified.

The first embodiment described above employs the following construction:that is, the refrigerant suction part 312 a, 313 a of the container 31a, 31 b is provided with the suction valve 312 c, 313 c; and therefrigerant discharge part 312 b, 313 b of the container 31 a, 31 b isprovided with the discharge valve 312 d, 313 d, whereby in each of therefrigerant circuits 4, 5, the refrigerant flows in one direction inorder of the refrigerant ports 312, 313 of the container 31 a, 31 b, therefrigerant flow-in port 12 a, 13 a of the heat exchanger 12, 13, therefrigerant flow-out port 12 b, 13 b of the heat exchanger 12, 13, andthe refrigerant ports 312, 313 of the container 31 a, 31 b.

In contrast to this, the present embodiment employs a construction inwhich the suction valve 312 c, 313 c and the discharge valve 312 d, 313d are eliminated, instead, the high temperature side refrigerant circuit4 is provided with check valves 44, 45 and the low temperature siderefrigerant circuit 5 is provided with check valves 56, 57.

Specifically, as shown in FIG. 8, in the high temperature siderefrigerant circuit 4, a first check valve 44 for allowing therefrigerant to flow from the refrigerant ports 312 of the hightemperature side container 31 a to the refrigerant flow-in port 13 a ofthe heating heat exchanger 13 is interposed between the refrigerantports 312 of the high temperature side container 31 a and therefrigerant flow-in port 13 a of the heating heat exchanger 13. Further,in the high temperature side refrigerant circuit 4, a second check valve45 for allowing the refrigerant to flow from the refrigerant flow-outport 13 b of the heating heat exchanger 13 to the refrigerant ports 312of the high temperature side container 31 a is interposed between therefrigerant flow-out port 13 b of the heating heat exchanger 13 and therefrigerant ports 312 of the high temperature side container 31 a.

On the other side, in the low temperature side refrigerant circuit 5, athird check valve 56 for allowing the refrigerant to flow from therefrigerant ports 313 of the low temperature side container 31 b to therefrigerant flow-in port 13 a of the cooling heat exchanger 12 isinterposed between the refrigerant ports 313 of the low temperature sidecontainer 31 b and the refrigerant flow-in port 13 a of the cooling heatexchanger 12. Further, in the low temperature side refrigerant circuit5, a fourth check valve 57 for allowing the refrigerant to flow from therefrigerant flow-out port 13 b of the cooling heat exchanger 12 to therefrigerant ports 313 of the low temperature side container 31 b isinterposed between the refrigerant flow-out port 13 b of the coolingheat exchanger 12 and the refrigerant ports 313 of the low temperatureside container 31 b.

According to this construction, after the magnetic field is applied tothe magnetic working material 30, the refrigerant near the hightemperature side ports 312, whose temperature is increased by the hotheat generated in the magnetic working material 30 by applying themagnetic field, can be made to surely flow into the heating heatexchanger 13 and the refrigerant flowing out of the heating heatexchanger 13 can be sucked into the working chambers 311 of the heatexchanger container 31.

Similarly, after the magnetic field is removed from the magnetic workingmaterial 30, the refrigerant near the low temperature side ports 313,whose temperature is decreased by the cold heat generated in themagnetic working material 30 by removing the magnetic field, can be madeto surely flow into the cooling heat exchanger 12 and the refrigerantflowing out of the cooling heat exchanger 12 can be sucked into theworking chambers 311 of the heat exchanger container 31.

In this regard, in the present embodiment, the first and the secondcheck valves 44, 45 disposed in the high temperature side refrigerantcircuit 4 may correspond to a first backward flow preventing part of thepresent disclosure, and the third and the fourth check valves 56, 57disposed in the low temperature side refrigerant circuit 5 maycorrespond to a second backward flow preventing part of the presentdisclosure.

Third Embodiment

Next, a third embodiment of the present disclosure will be described onthe basis of FIG. 9. FIG. 9 is a general construction diagram of avehicle air conditioning device 1 of the present embodiment. In thepresent embodiment, the descriptions of parts identical or equivalent tothe parts in the first and the second embodiments will be omitted orsimplified.

The second embodiment described above employs a construction in whichthe high temperature side refrigerant circuit 4 is provided with thefirst and the second check valves 44, 45 and in which the lowtemperature side refrigerant circuit 5 is provided with the third andthe fourth check valves 56, 57. In contrast to this, the presentembodiment employs a construction in which the refrigerant circuit 4 isprovided with opening and closing valves 46, 47 and the refrigerantcircuit 5 is provided with opening and closing valves 58, 59, theopening and closing valves being opened or closed according to a controlsignal from the air conditioning control device 100, in place of therespective check valves 44, 45 and 56, 57.

Specifically, as shown in FIG. 9, in the high temperature siderefrigerant circuit 4, a first opening and closing valve 46 isinterposed between the refrigerant ports 312 of the high temperatureside container 31 a and the refrigerant flow-in port 13 a of the heatingheat exchanger 13, and a second opening and closing valve 47 isinterposed between the refrigerant flow-out port 13 b of the heatingheat exchanger 13 and the refrigerant ports 312 of the high temperatureside container 31 a.

In this regard, the first opening and closing valve 46 is controlled bythe air conditioning control device 100 in such a way as to allow therefrigerant to flow only from the refrigerant ports 312 of the hightemperature side container 31 a to the refrigerant flow-in port 13 a ofthe heating heat exchanger 13. Further, the second opening and closingvalve 47 is controlled by the air conditioning control device 100 insuch a way as to allow the refrigerant to flow only from the refrigerantflow-out port 13 b of the heating heat exchanger 13 to the refrigerantports 312 of the high temperature side container 31 a.

On the other hand, in the low temperature side refrigerant circuit 5, athird opening and closing valve 58 is interposed between the refrigerantports 313 of the low temperature side container 31 b and the refrigerantflow-in port 13 a of the cooling heat exchanger 12, and a fourth openingand closing valve 59 is interposed between the refrigerant flow-out port13 b of the cooling heat exchanger 12 and the refrigerant ports 313 ofthe low temperature side container 31 b.

In this regard, the third opening and closing valve 58 is controlled bythe air conditioning control device 100 in such a way as to allow therefrigerant to flow only from the refrigerant ports 313 of the lowtemperature side container 31 b to the refrigerant flow-in port 13 a ofthe cooling heat exchanger 12. Further, the fourth opening and closingvalve 59 is controlled by the air conditioning control device 100 insuch a way as to allow the refrigerant to flow only from the refrigerantflow-out port 13 b of the cooling heat exchanger 12 to the refrigerantports 313 of the low temperature side container 31 b.

Also according to this construction, the same advantages as the secondembodiment can be produced. In this regard, the first and the secondopening and closing valves 46, 47 disposed in the high temperature siderefrigerant circuit 4 in the present embodiment may correspond to thefirst backward flow preventing part of the present disclosure, and thethird and the fourth opening and closing valves 58, 59 disposed in thelow temperature side refrigerant circuit 5 in the present embodiment maycorrespond to the second backward flow preventing part of the presentdisclosure.

Fourth Embodiment

Next, a fourth embodiment of the present disclosure will be described onthe basis of FIG. 10. FIG. 10 is a general construction diagram of avehicle air conditioning device 1 of the present embodiment.

In the present embodiment, the magnetic refrigeration system 2 having arefrigerant circuit of only the cooling mode for cooling the interior ofpassenger compartment will be described. In this regard, in the presentembodiment, the descriptions of parts identical or equivalent to theparts in the first to the third embodiments will be omitted orsimplified.

The magnetic refrigeration system 2 of the present embodiment, as shownin FIG. 10, is constructed of: the magnetic refrigerator 3; a heatradiation side refrigerant circuit (first refrigerant circulationcircuit) 8 for circulating the refrigerant having temperature increasedby the hot heat generated by the magnetic refrigerator 3 to a heatradiator (first heat exchanger) 7; and a low temperature siderefrigerant circuit (second refrigerant circulation circuit) 5 forcirculating the refrigerant having temperature decreased by the clodheat generated by the magnetic refrigerator 3 to the cooling heatexchanger (second heat exchanger) 12.

The heat exchange container 31 of the magnetic refrigerator 3 of thepresent embodiment is constructed of a hollow cylindrical containerhaving working chambers 311 formed therein, the working chamber 311having the magnetic working material 30 received therein and having therefrigerant flowing therethrough. The heat exchange container 31 has therefrigerant pump 34 coaxially arranged on one end side thereof.

The heat exchange container 31 has the refrigerant ports 312 formed inits end face opposite to the refrigerant pump 34, and has communicationpassages 314 formed in its end face adjacent to the refrigerant pump 34,the communication passage 314 communicating with the cylinder bore 344of the refrigerant pump 34.

The refrigerant pump 34 of the present embodiment is constructed of afirst bore part 344 a corresponding to the communication passages 314 ofthe heat exchange container 31, and a second bore part 344 bcommunicating with the low temperature side refrigerant circuit 5 whichwill be described later. In this regard, the cylinder bore 344 isconstructed in such a way that the refrigerant in the first bore part344 a and the refrigerant in the second bore part 344 b can flow,whereby the heat of the first bore part 344 a is directly transported tothe second bore part 344 b.

In this regard, each communication passage 345 for making the secondbore part 344 b to communicate with the low temperature side refrigerantcircuit 5 is constructed of a refrigerant suction part 345 a for suckingthe refrigerant from the low temperature side refrigerant circuit 5 anda refrigerant discharge part 345 b for discharging the refrigerant tothe low temperature side refrigerant circuit 5. The refrigerant suctionpart 345 a of the communication passage 345 is provided with a suctionvalve 345 c opened when the refrigerant is sucked, and the refrigerantdischarge part 345 b of the communication passage 345 is provided with adischarge valve 345 d opened when the refrigerant is discharged. Here,in the present embodiment, the communication passages 345 communicatingwith the low temperature side refrigerant circuit 5 in the refrigerantpump 34 construct refrigerant ports corresponding to the refrigerantports 312 in the heat exchange container 31.

The heat radiation side refrigerant circuit 8 is a refrigerantcirculation circuit for introducing the refrigerant discharged from therefrigerant discharge parts 312 b of the refrigerant ports 312 in theheat exchange container 31 into a refrigerant flow-in port 7 a of theheat radiator 7 and for returning the refrigerant flowing out of arefrigerant flow-out port 13 b of the heat radiator 7 to the refrigerantsuction parts 312 a of the refrigerant ports 312 in the heat exchangecontainer 31.

Thus, in the heat radiation side refrigerant circuit 8, the refrigerantis circulated in order of the refrigerant discharge parts 312 b of theheat exchange container 31, the heat radiator 7, and the refrigerantsuction parts 312 a of the heat exchange container 31. In this regard,the heat radiator 7 is a heat exchanger that is arranged in the enginecompartment and that makes the refrigerant flowing therein through therefrigerant flow-in port 7 a exchange heat with the outside air.

Further, the low temperature side refrigerant circuit 5 of the presentembodiment is a refrigerant circulation circuit for introducing therefrigerant discharged from the refrigerant discharge parts 345 b of thecommunication passages 345 in the refrigerant pump 34 into therefrigerant flow-in port 12 a of the cooling heat exchanger 12 and forreturning the refrigerant flowing out of the refrigerant flow-out port12 b of the cooling heat exchanger 12 to the refrigerant suction parts345 a of the communication passages 345 in the refrigerant pump 34.

Thus, in the low temperature side refrigerant circuit 5, the refrigerantis circulated in order of the refrigerant discharge parts 345 b of thecommunication passages 345 in the refrigerant pump 34, the cooling heatexchanger 12, and the refrigerant suction parts 345 a of thecommunication passages 345 in the refrigerant pump 34.

Next, the operation of the magnetic refrigerator 3 in the refrigerationsystem 2 of the present embodiment will be generally described.

When the piston 343 in the first bore part 344 a in the refrigerant pump34 is positioned near the bottom dead center and the permanent magnet323 a comes near to the upper working chambers 311 of the heat exchangecontainer 31, the magnetic field is applied to the magnetic workingmaterial 30 received in the upper working chambers 311 and therefrigerant in the upper working chambers 311 is increased intemperature (the magnetic field applying process). At this time, thepiston 343 in the second bore part 344 b is positioned near the top deadcenter.

Then, when the piston 343 in the first bore part 344 a is moved from thebottom dead center to the top dead center, the refrigerant in the upperworking chambers 311 is transferred from the refrigerant pump 34 to therefrigerant ports 312 and the high temperature refrigerant near therefrigerant discharge parts 312 b is discharged to the heat radiator 7(refrigerant discharging process). At this time, the piston 343 in thesecond bore part 344 b is moved from the top dead center to the bottomdead center and the refrigerant flowing out of the cooling heatexchanger 12 is sucked into the second bore part 344 b via therefrigerant suction parts 345 a of the communication passages 345.

Then, when the piston 343 in the first bore part 344 a is positionednear the top dead center and the permanent magnet 323 a is moved awayfrom the upper working chambers 311 in the heat exchange container 31,the magnetic field is removed from the magnetic working material 30received in the upper working chambers 311, whereby the refrigerant inthe upper working chambers 311 is decreased in temperature (magneticfield removing process). At this time, the piston 343 in the second borepart 344 b is positioned near the bottom dead center. In this regard,the refrigerant in the first bore part 344 a whose temperature isdecreased by removing the magnetic field from the magnetic workingmaterial 30 flows into the second bore part 344 b, whereby therefrigerant in the second bore 344 b is decreased in temperature.

Then, the piston 343 in the first bore part 344 a is moved from the topdead center to the bottom dead center and the refrigerant flowing out ofthe heating heat exchanger 13 is sucked into portions near therefrigerant suction parts 312 a. At this time, the piston 343 in thesecond bore part 344 b is moved from the bottom dead center to the topdead center and the refrigerant in the second bore part 344 b isdischarged to the cooling heat exchanger 12 via the refrigerantdischarge parts 345 b of the communication passages 345.

In this way, by these four processes of the magnetic field applyingprocess, the refrigerant discharging process, the magnetic fieldremoving process, and the refrigerant sucking process, the cold heatgenerated by the magnetocaloric effect of the magnetic working material30 received in the upper working chambers 311 of the heat exchangecontainer 31 is transported to the cooling heat exchanger 12. In thisway, the blown air to be blown into the passenger compartment can becooled in the cooling heat exchanger 12. In this regard, the hot heatgenerated by the magnetocaloric effect of the magnetic working material30 received in the upper working chambers 311 of the heat exchangecontainer 31 is transported to the heat radiator 7 and is radiated tothe outside air.

According to the present embodiment described above, the refrigeranthaving temperature decreased by the cold heat generated in the magneticworking material 30 can be made to directly flow into the cooling heatexchanger 12, so that a heat exchanger loss caused when the cold heatgenerated in the magnetic working material 30 is transported can bereduced and hence the COP of the magnetic refrigeration system can beimproved.

In this regard, although the magnetic refrigeration system 2 having therefrigerant circuit of only the cooling mode for cooling the interior ofthe passenger compartment has been described in the present embodiment,the magnetic refrigeration system 2 may have a construction having arefrigerant circuit of only the heating mode for heating the interior ofthe passenger compartment. In this case, the following construction isrecommended: for example, the heat radiator 7 of the present embodimentis arranged in the case 11 of the indoor air conditioning unit 10 and isfunctioned as a heating heat exchanger for heating the blown air to beblown into the passenger compartment, and the cooling heat exchanger 12is arranged in the engine compartment and is functioned as a heatabsorber for exchanging heat with the outside air.

Fifth Embodiment

Next, a fifth embodiment of the present disclosure will be described onthe basis of FIG. 11 and FIG. 12. FIG. 11 is a general constructiondiagram of a vehicle air conditioning device 1 of the presentembodiment, and FIG. 12 is an enlarged view of a magnetic refrigeratorof the present embodiment.

The present embodiment is different from the first to the fourthembodiments in the specific construction of the one and the otherrefrigerant ports 312, 313 in the magnetic refrigerator 3 and in thespecific construction of the refrigerant pump 34. In this regard, in thepresent embodiment, the descriptions of parts identical or equivalent tothe parts in the first to the fourth embodiments will be omitted orsimplified.

As shown in FIG. 11 and FIG. 12, in each of the refrigerant ports 312,313 of the present embodiment, the respective refrigerant suction parts312 a, 313 a are disposed on the same circumference when viewed from thelongitudinal direction of the heat exchange container 31. Further, therespective refrigerant discharge parts 312 b, 313 b are disposed on thesame circumference when viewed from the longitudinal direction of theheat exchange container 31. In the present embodiment, the refrigerantdischarge parts 312 b, 313 b are arranged in such a way as to bepositioned on the outer side in the radial direction of the heatexchange container 31 as compared with the refrigerant suction parts 312a, 313 a. Here, the refrigerant suction parts 312 a, 313 a may bearranged in such a way as to be positioned on the outer side in theradial direction of the heat exchange container 31 as compared with therefrigerant discharge parts 312 b, 313 b.

Each of the refrigerant suction parts 312 a, 313 a is provided with thesuction valve 313 c and each of the refrigerant discharge parts 312 b,313 b is provided with the discharge valve 313 d. Here, the respectivesuction valves 313 c are disposed in such a way as to be positioned onthe same circumference when viewed from the longitudinal direction ofthe heat exchange container 31 in correspondence to the refrigerantsuction parts 312 a, 313 a. Similarly, the respective discharge valves313 d are disposed in such a way as to be positioned on the samecircumference when viewed from the longitudinal direction of the heatexchange container 31 in correspondence to the refrigerant dischargeparts 312 b, 313 b.

The respective refrigerant suction parts 312 a in the high temperatureside ports 312 communicate with each other via a suction side manifold312 e, whereas the respective discharge parts 312 b in the hightemperature side ports 312 communicate with each other via a dischargeside manifold 312 f. Similarly, the respective refrigerant suction parts313 a in the low temperature side ports 313 communicate with each othervia a suction side manifold 313 e, whereas the respective dischargeparts 313 b in the low temperature side ports 313 communicate with eachother via a discharge side manifold 313 f. In this regard, a heatinsulating material (not shown) is arranged between the suction sidemanifold 312 e and the discharge side manifold 312 f in the hightemperature side ports 312, which hence inhibits heat transfer betweenthe both manifolds 312 e and 312 f. Similarly, a heat insulatingmaterial (not shown) is arranged between the suction side manifold 313 eand the discharge side manifold 313 f in the low temperature side ports313, which hence inhibits heat transfer between the both manifolds 313 eand 313 f.

Here, the volume of a space constructing each of the refrigerant suctionparts 312 a, 313 a and the refrigerant discharge parts 312 b, 313 b inthe heat exchange container 31 is made smaller than the volume of therefrigerant discharged at one time (that is, cylinder volume) in therefrigerant pump 34, which will be described later. Here, the volume ofthe space constructing each of the refrigerant suction parts 312 a, 313a and the refrigerant discharge parts 312 b, 313 b in the heat exchangecontainer 31 corresponds to the total volume of the volume (dead volume)of a space in which each of the valves 312 c, 313 c, 312 d, 313 d isarranged (including the movable range of each valve).

Further, the permanent magnets 323 a, 323 b constructing a portion ofthe magnetic field applying and removing device 32 are disposed atpositions shifted by 180° from each other in the outer circumferences ofthe rotors 322 a, 322 b, respectively. For example, as shown in FIG. 12,in the case where one permanent magnet 323 a is positioned on the upperside, the other permanent magnet 323 b is positioned on the lower side.

Next, describing the refrigerant pump 34 of the present embodiment, thepresent embodiment employs a radial piston pump of a multi-cylinder typein which the pistons 346 are slid in the radial direction with respectto the axial direction of the rotary shaft 321 a, 321 b.

Specifically, the refrigerant pump 34 of the present embodiment isconstructed of a cylindrical housing 340, a drive shaft rotatablysupported in the housing 340 and having an eccentric cam 348 integrallyformed, a plurality of cylinder bores 347 formed radially in the housing340, and the pistons 346 reciprocated in the respective cylinder bores347 according to the rotation of the eccentric cam 348. Here, in thepresent embodiment, the heat exchange container 31 is integrated withthe housing 340 of the refrigerant pump 34.

As are the cases with the refrigerant pump described in theabove-mentioned embodiments, the refrigerant pump 34 of the presentembodiment is constructed in such a way as to suck or discharge therefrigerant from or into the respective containers 31 a, 31 b insynchronization with applying and removing the magnetic field to andfrom the magnetic working material 30.

For example, when the magnetic field is applied to the magnetic workingmaterial 30 in the working chambers 311 positioned on the upper side inthe high temperature side container 31 a and the magnetic field isremoved from the magnetic working material 30 in the working chambers311 positioned on the upper side in the low temperature side container31 b, the refrigerant pump 34 discharges the refrigerant in sequenceinto the respective working chambers 311 positioned on the upper side inthe respective containers 31 a, 31 b and sucks the refrigerant insequence from the respective working chambers 311 positioned on thelower side in the respective containers 31 a, 31 b.

On the other hand, when the magnetic field is removed from the magneticworking material 30 in the working chambers 311 positioned on the upperside in the high temperature side container 31 a and the magnetic fieldis applied to the magnetic working material 30 in the working chambers311 positioned on the upper side in the low temperature side container31 b, the refrigerant pump 34 sucks the refrigerant in sequence from therespective working chambers 311 positioned on the upper side in therespective containers 31 a, 31 b and discharges the refrigerant insequence into the respective working chambers 311 positioned on thelower side in the respective containers 31 a, 31 b.

In this way, in the magnetic refrigerator 3, the refrigerant can besucked or discharged in sequence from or into the respective workingchambers 311 in the respective containers 31 a, 31 b in synchronizationwith applying and removing the magnetic field to and from the magneticworking material 30, so that the refrigerant near the refrigerantdischarge parts 312 b, 313 b in the respective containers 31 a, 31 b canbe continuously discharged to the outside.

Next, the operation of the magnetic refrigerator 3 according to thepresent embodiment will be generally described. When the piston 346 inthe cylinder bore 347 positioned on the upper side in the refrigerantpump 34 is positioned near the bottom dead center and the permanentmagnet 323 a comes near to the upper working chambers 311 positioned onthe upper side of the high temperature side container 31 a, the magneticfield is applied in sequence to the magnetic working material 30received in the upper working chambers 311 positioned on the upper side(that is, the magnetic working material 30 is magnetized, the magneticfield applying process). At this time, the magnetic working material 30generates heat by the magnetocaloric effect, whereby the refrigerant inthe respective working chambers 311 positioned on the upper side issequentially increased in temperature.

Then, the piston 346 in the cylinder bore 347 positioned on the upperside in the refrigerant pump 34 is moved from the bottom dead center tothe top dead center and the refrigerant in the respective workingchambers 311 positioned on the upper side is transferred from therefrigerant pump 34 to the high temperature side ports 312. At thistime, the discharge valves 312 d disposed at the refrigerant dischargeparts 312 b of the high temperature side ports 312 are opened and hencethe high temperature refrigerant near the refrigerant discharge parts312 b is discharged to the heating heat exchanger 13 via the dischargeside manifolds 312 f (refrigerant discharging process).

Then, when the piston 346 in the cylinder bore 347 positioned on theupper side in the refrigerant pump 34 is positioned near the top deadcenter and the permanent magnet 323 a is moved away from the respectiveworking chambers 311 positioned on the upper side of the hightemperature side container 31 a, the magnetic field is removed from themagnetic working material 30 received in the respective working chambers311 positioned on the upper side (that is, the magnetic working material30 is demagnetized, magnetic field removing process).

Then, the piston 346 in the cylinder bore 347 positioned on the upperside in the refrigerant pump 34 is moved from the top dead center to thebottom dead center and the refrigerant in the respective workingchambers 311 positioned on the upper side is transferred from the hightemperature side ports 312 to the refrigerant pump 34. At this time, thesuction valves 312 c disposed at the refrigerant suction parts 312 a ofthe high temperature side ports 312 are opened and the refrigerantflowing out of the heating heat exchanger 13 is sucked into portionsnear the refrigerant suction parts 312 a via the suction side manifolds312 e (refrigerant sucking process). Then, when the piston 346 of therefrigerant pump 34 is returned to a position near the bottom deadcenter, there is again brought about the magnetic field applyingprocess.

In this way, when these four processes of the magnetic field applyingprocess, the refrigerant discharging process, the magnetic fieldremoving process, and the refrigerant sucking process are repeated insequence in the respective working chambers 311 of the high temperatureside container 31 a, the hot heat generated by the magnetocaloric effectof the magnetic working material 30 received in the respective workingchambers 311 of the high temperature side container 31 a can betransported to the heating heat exchanger 13.

On the other hand, when the magnetic field is applied to the magneticworking material 30 in the respective working chambers 311 positioned onthe upper side of the high temperature side container 31 a, in therespective working chambers 311 positioned on the upper side of the lowtemperature side container 31 b, the permanent magnet 323 b gets faraway from the working chambers 311 and hence the magnetic field isremoved in sequence from the magnetic working material 30 received inthe respective working chambers 311 positioned on the upper side(magnetic field removing process).

Then, the piston 346 in the cylinder bore 347 positioned on the upperside in the refrigerant pump 34 is moved from the bottom dead center tothe top dead center and the refrigerant in the respective workingchambers 311 positioned on the upper side is transferred from therefrigerant pump 34 to the low temperature side ports 313. At this time,the discharge valves 313 d disposed at the refrigerant discharge parts313 b of the low temperature side ports 313 are opened and the lowtemperature refrigerant near the refrigerant discharge parts 313 b isdischarged to the cooling heat exchanger 12 via the discharge sidemanifolds 313 f (refrigerant discharging process).

Further, when the piston 346 in the cylinder bore 347 positioned on theupper side in the refrigerant pump 34 is moved near the top dead centerand the permanent magnet 323 b comes near the respective workingchambers 311 positioned on the upper side of the low temperature sidecontainer 31 b, the magnetic field is applied to the magnetic workingmaterial 30 received in the respective working chambers 311 positionedon the upper side (magnetic field applying process).

Then, the piston 346 in the cylinder bore 347 positioned on the upperside in the refrigerant pump 34 is moved from the top dead center to thebottom dead center and the refrigerant in the respective workingchambers 311 positioned on the upper side is transferred from the lowtemperature side ports 313 to the refrigerant pump 34. At this time, thesuction valves 313 c disposed at the refrigerant suction parts 313 a ofthe low temperature side ports 313 are opened and the refrigerantflowing out of the cooling heat exchanger 12 is sucked into portionsnear the refrigerant suction parts 313 a via the suction side manifolds313 e (refrigerant sucking process). Then, when the piston 346 of therefrigerant pump 34 is returned near the bottom dead center, there isagain brought about the magnetic field removing process.

In this way, when these four processes of the magnetic field removingprocess, the refrigerant discharging process, the magnetic fieldapplying process, and the refrigerant sucking process are repeated insequence in the respective working chambers 311 of the low temperatureside container 31 b, the cold heat generated by the magnetocaloriceffect of the magnetic working material 30 received in the respectiveworking chambers 311 of the low temperature side container 31 b can betransported to the cooling heat exchanger 12.

In the magnetic refrigeration system of the present embodiment describedabove, the refrigerant having temperature increased by the hot heatgenerated in the magnetic working material 30 can be made to directlyflow into the heating heat exchanger 13, and the refrigerant havingtemperature decreased by the cold heat generated in the magnetic workingmaterial 30 can be made to directly flow into the cooling heat exchanger12, so that the same advantages as the first embodiment described abovecan be produced.

In addition to this, in the present embodiment, the volume of a spaceconstructing each of the refrigerant suction parts 312 a, 313 a and therefrigerant discharge parts 312 b, 313 b in the heat exchange container31 is made smaller than the volume of the refrigerant discharged at onetime (that is, cylinder volume) in the refrigerant pump 34. For thisreason, it is possible to prevent the refrigerant, whose temperature isincreased by the hot heat generated in the magnetic working material 30,and the refrigerant, whose temperature is decreased by the cold heatgenerated in the magnetic working material 30, from remaining in theheat exchange container 31 and hence to efficiently transport the hotheat and the cold heat generated in the magnetic working material 30 tothe outside of the heat exchange container 31.

Sixth Embodiment

Next, a sixth embodiment of the present disclosure will be described onthe basis of FIG. 13. FIG. 13 is a general construction diagram of avehicle air conditioning device 1 of the present embodiment. Here, inthe present embodiment, the descriptions of parts identical orequivalent to the parts in the first to the fifth embodiments will beomitted or simplified.

The present embodiment employs a construction in which the suctionvalves 312 c, 313 c, which are disposed respectively in the refrigerantsuction parts 312 a, 313 a, and the discharge valves 312 d, 313 d, whichare disposed respectively in the refrigerant discharge parts 312 b, 313b, in the fifth embodiment are eliminated and in which check valves 44,45 and 56, 57 are provided in place of those valves.

Specifically, each of the refrigerant suction parts 312 a of the hightemperature side container 31 a is provided with a first check valve 44for allowing the refrigerant to flow from the refrigerant flow-out port13 b of the heating heat exchanger 13 to each of the refrigerant suctionparts 312 a of the high temperature side container 31 a, whereas each ofthe refrigerant discharge parts 312 b of the high temperature sidecontainer 31 a is provided with a second check valve 45 for allowing therefrigerant to flow from each of the refrigerant discharge parts 312 bof the high temperature side container 31 a to the refrigerant flow-inport 13 a of the heating heat exchanger 13.

Similarly, each of the refrigerant suction parts 313 a of the lowtemperature side container 31 b is provided with a third check valve 56for allowing the refrigerant to flow from the refrigerant flow-out port12 b of the cooling heat exchanger 12 to each of the refrigerant suctionparts 313 a of the low temperature side container 31 b, whereas each ofthe refrigerant discharge parts 313 b of the low temperature sidecontainer 31 b is provided with a fourth check valve 57 for allowing therefrigerant to flow from each of the refrigerant discharge parts 313 bof the low temperature side container 31 b to the refrigerant flow-inport 12 a of the cooling heat exchanger 12.

Here, the respective first and third check valves 44, 56 disposed at therespective refrigerant suction parts 312 a, 313 a are arranged in such away as to be positioned on the same circumference when the heat exchangecontainer 31 is viewed from the longitudinal direction in correspondenceto the refrigerant suction parts 312 a, 313 a. Further, the respectivesecond and fourth check valves 45, 57 disposed at the respectiverefrigerant discharge parts 312 b, 313 b are arranged in such a way asto be positioned on the same circumference when the heat exchangecontainer 31 is viewed from the longitudinal direction in correspondenceto the refrigerant discharge parts 312 b, 313 b.

Also according to this construction, the refrigerant having temperatureincreased by the hot heat generated in the magnetic working material 30can be made to directly flow into the heating heat exchanger 13, and therefrigerant having temperature decreased by the cold heat generated inthe magnetic working material 30 can be made to directly flow into thecooling heat exchanger 12, so that the same advantages as the fifthembodiment described above can be produced.

Seventh Embodiment

Next, a seventh embodiment of the present disclosure will be describedon the basis of FIG. 14. FIG. 14 is a general construction diagram of avehicle air conditioning device 1 of the present embodiment. Here, inthe present embodiment, the descriptions of parts identical orequivalent to the parts in the first to the sixth embodiments will beomitted or simplified.

The present embodiment employs a construction in which the check valves44, 45, which are disposed in the respective refrigerant suction parts312 a, 313 a and the check valves 56, 57, which are disposed in therespective refrigerant discharge parts 312 b, 313 b, in the sixthembodiment are eliminated and in which opening and closing valves 46, 47and 58, 59, which are opened or closed according to a control signalfrom the air conditioning control device 110, are provided in place ofthose check valves 44, 45 and 56, 57.

Specifically, each of the refrigerant suction parts 312 a of the hightemperature side container 31 a is provided with a first opening andclosing valve 46 controlled in such a way as to allow the refrigerant toflow only from the refrigerant flow-out port 13 b of the heating heatexchanger 13 to each of the refrigerant suction parts 312 a of the hightemperature side container 31 a, whereas each of the refrigerantdischarge parts 312 b of the high temperature side container 31 a isprovided with a second opening and closing valve 47 controlled in such away as to allow the refrigerant to flow only from the refrigerantdischarge part 312 b of the high temperature side container 31 a to therefrigerant flow-in port 13 a of the heating heat exchanger 13.

Similarly, each of the refrigerant suction parts 313 a of the lowtemperature side container 31 b is provided with a third opening andclosing valve 58 controlled in such a way as to allow the refrigerant toflow only from the refrigerant flow-out port 12 b of the cooling heatexchanger 12 to each of the refrigerant suction parts 313 a of the lowtemperature side container 31 b, whereas each of the refrigerantdischarge parts 313 b of the low temperature side container 31 b isprovided with a fourth opening and closing valve 59 controlled in such away as to allow the refrigerant to flow only from each of therefrigerant discharge parts 313 b of the low temperature side container31 b to the refrigerant flow-in port 12 a of the cooling heat exchanger12.

In this regard, the respective first and third opening and closingvalves 46, 58 disposed at the respective refrigerant suction parts 312a, 313 a are arranged in such a way as to be positioned on the samecircumference when the heat exchange container 31 is viewed from thelongitudinal direction in correspondence to the refrigerant suctionparts 312 a, 313 a. Further, the respective second and fourth openingand closing valves 47, 59 disposed at the respective refrigerantdischarge parts 312 b, 313 b are arranged in such a way as to bepositioned on the same circumference when the heat exchange container 31is viewed from the longitudinal direction in correspondence to therefrigerant discharge parts 312 b, 313 b.

Also according to this construction, the refrigerant having temperatureincreased by the hot heat generated in the magnetic working material 30can be made to directly flow into the heating heat exchanger 13, and therefrigerant having temperature decreased by the cold heat generated inthe magnetic working material 30 can be made to directly flow into thecooling heat exchanger 12, so that the same advantages as the fifth andsixth embodiments described above can be produced.

Eighth Embodiment

In the fifth embodiment described above, as shown in FIG. 12, thesuction valves 312 c, 313 c are arranged nearer to the working chambers311 than the discharge valves 312 d, 313 d are. For this reason, whenthe refrigerant is discharged from each of the discharge valves 312 d,313 d, the refrigerant remaining in a dead space around each of thesuction valves 312 c, 313 c and the refrigerant discharged from each ofthe discharge valves 312 c, 313 c are likely to be mixed with each otherand to unnecessarily exchange heat between them.

Hence, an eighth embodiment employs a construction in which thedischarge valves 312 d, 313 d are arranged nearer to the workingchambers 311 in the longitudinal direction of the heat exchangecontainer 31 than the suction valves 312 c, 313 c are. In other words,the discharge valves 312 d, 313 d are arranged in the vicinity of theworking chambers 311.

As shown by a partial enlarged section view in FIG. 15, in the presentembodiment, the refrigerant suction parts 312 a, 313 a are arranged onthe outer side in the radial direction of the heat exchange container 31as compared with the refrigerant discharge parts 312 b, 313 b.

A plate-shaped valve plate 316 having a suction hole 316 a and adischarge hole 316 b formed therein is arranged at a position adjacentto the working chambers 311. Here, the suction hole 316 a formed in thevalve pate 316 constructs a communication hole for sucking therefrigerant into the working chamber 311 and the discharge hole 316 bconstructs a communication hole for discharging the refrigerant from theworking chamber 311.

The discharge valves 312 d, 313 d are arranged at positions adjacent tothe valve plate 316 and the suction valves 312 c, 313 c are arranged atpositions away from the valve plate 316 by a distance more than amovable range of the valve. In other words, the discharge valve 312 d,313 d is constructed in such a way as to directly open or close thedischarge hole 316 b of the valve plate 316 and the suction valve 312 c,313 c is constructed in such a way as to indirectly open or close thesuction hole 316 a of the valve plate 316.

In this way, when the discharge valve 312 d, 313 d is arranged close tothe working chamber 311, it is possible to prevent an unnecessary heatexchange between the refrigerant remaining around the suction valve 312c, 313 c and the refrigerant discharged from the working chamber 311 viathe discharge valve 312 d, 313 d. This can reduce a heat exchange lossat the time of transporting the hot heat and the cold heat generated inthe magnetic working material 30 and hence can improve the COP of themagnetic refrigeration system.

Ninth Embodiment

In the present embodiment will be described an example in which therespective valves 312 c, 312 d are constructed of a rotary valve and inwhich the respective valves 313 c, 313 d are constructed of a rotaryvalve.

As shown by an enlarged view of a magnetic refrigerator 3 in FIG. 16,one rotary valve constructs the valves 312 c, 312 d and the other rotaryvalve constructs the valves 313 c, 313 d. Each of the rotary valves isconstructed of a valve plate 317 and a rotary disk 318. The valve plate317 is arranged adjacently to the working chambers 311, and has suctionholes 317 a and discharge holes 317 b formed therein. Each of thesuction holes 317 a and discharge holes 317 b communicates with each ofthe working chambers 311. The rotary disk 318 rotates in acircumferential direction of the heat exchange container 31 and opens orcloses the suction holes 317 a and the discharge holes 317 b of thevalve plate 317.

Each of the suction holes 317 a formed in the valve plate 317 constructsa communication hole for sucking the refrigerant into each of theworking chambers 311, and each of the discharge holes 317 b constructs acommunication hole for discharging the refrigerant from each of theworking chambers 311.

As shown in FIG. 17 by a section view taken on a line B-B in FIG. 16 andshown in FIG. 18 by a section view taken on a line C-C in FIG. 16, therotary disk 318 is coupled to the rotary shaft 321 a, 321 b in such away as to be rotated by power supplied from the electric motor 35 whichis a drive part and is constructed in such a way as to open or close thesuction holes 317 a and the discharge holes 317 b of the valve plate 317at timings shifted from each other in synchronization with the rotationof the rotary shaft 321 a, 321 b.

Specifically, the rotary disk 318 has suction side through holes 318 apassed through from an obverse to a reverse at positions, which areopposite to the suction holes 317 a of the valve plate 317 in the axialdirection when the refrigerant is sucked into the working chambers 311.Similarly, the rotary disk 318 has discharge side through holes 318 bpassed through from an obverse to a reverse at positions, which areopposite to the discharge holes 317 b of the valve plate 317 in theaxial direction when the refrigerant is discharged from the workingchambers 311.

As is the case with the present embodiment, in the case where therespective valves 312 c, 312 d are constructed of the rotary valve andwhere the respective valves 313 c, 313 d are constructed of the rotaryvalve, it is possible to prevent the refrigerant from remaining aroundthe respective suction valves 312 c, 313 c. Hence, it is possible toprevent an unnecessary heat exchange between the refrigerant remainingaround the suction valve 312 c, 313 c and the refrigerant dischargedfrom the working chamber 311 via the discharge valve 312 d, 313 d. Inthis way, it is possible to reduce a heat exchange loss at the time oftransporting the hot heat and the cold heat generated in the magneticworking material 30 and hence to improve the COP of the magneticrefrigeration system.

Further, the present embodiment employs a construction in which therotary disk 318 of the rotary valve is rotated by the power for drivingthe magnetic field applying and removing device 32, that is, the powerof the electric motor 35, the magnetic refrigeration system can berealized by a simple construction. Still further, the suction valves 312c and the discharge valves 312 d can be integrally constructed and thesuction valves 313 c and the discharge valves 313 d can be integrallyconstructed. Hence, the magnetic refrigeration system can be realized bya further simpler construction.

Tenth Embodiment

In the present embodiment will be described an example in which each ofthe suction valves 312 c, 313 c is constructed of a rotary valve and inwhich each of the discharge valves 312 d, 313 d is constructed of a reedvalve.

As shown by an enlarged view of a magnetic refrigerator in FIG. 19, therotary valve constructing the respective suction valve 312 c, 313 c isconstructed of a valve plate 317 and a rotary disk 318. The valve plate317 is arranged adjacently to the working chambers 311 and has suctionholes 317 a each of which communicates with each of the working chambers311. The rotary disk 318 rotates in a circumferential direction of theheat exchange container 31 and opens or closes the suction holes 317 aof the valve plate 317.

As shown in FIG. 20 by a section view taken on a line D-D in FIG. 19 andin FIG. 21 by a section view taken on a line E-E in FIG. 19, the rotarydisk 318 is coupled to the rotary shaft 321 a, 321 b in such a way as tobe rotated by power supplied from the electric motor 35 corresponding tothe drive part and is constructed in such a way as to open or close thesuction holes 317 a of the valve plate 317 in synchronization with therotation of the rotary shaft 321 a, 321 b. In this regard, in the rotarydisk 318 are formed suction side through holes 318 a each of which ispassed through from an obverse to a reverse at a position opposite tothe suction hole 317 a of the valve plate 317 in the axial directionwhen the refrigerant is sucked into each of the working chambers 311.

Here, the reed valve constructing the discharge valve 312 d, 313 d isconstructed in such a way as to open or close each of discharge holes317 b formed in the valve plate 317 by an elastic plate member.

As is the case with the present embodiment, even in the case where onlythe suction valve 312 c, 313 c is constructed of the rotary valve, it ispossible to prevent the refrigerant from remaining around the suctionvalve 312 c, 313 c and hence to prevent an unnecessary heat exchangebetween the refrigerant remaining around the suction valve 312 c, 313 cand the refrigerant discharged from the working chamber 311 via thedischarge valve 312 d, 313 d. In this way, it is possible to reduce aheat exchange loss at the time of transporting the hot heat and the coldheat generated in the magnetic working material 30 and hence to improvethe COP of the magnetic refrigeration system.

11th Embodiment

The first and the second backward flow preventing parts are respectivelyconstructed of the check valves 44, 45 and 56, 57 in the second and thesixth embodiments. Alternatively, each of the first and the secondbackward flow preventing parts may be constructed of a fluid diode inwhich resistance is smaller in a forward direction of a refrigerant flowthan in a backward direction of the refrigerant flow. According to thisconstruction, the magnetic refrigeration system can be realized by asimple construction. Here, one of the first and the second backward flowpreventing parts may be constructed of a fluid diode 71, 72.

Here, as the fluid diode can be employed a nozzle type fluid diode 71 ora vortex type fluid diode 72.

FIG. 22 is a schematic section view of the nozzle type fluid diode 71.The nozzle type fluid diode 71 is constructed of a cylindrical memberand, as shown in FIG. 22, is constructed of a tapered part 71 a whosesize is decreased in a conical shape from an upstream side of arefrigerant flow to a downstream side of the refrigerant flow in arefrigerant flow passage.

In this nozzle type fluid diode 71, resistance at the tapered part 71 abecomes larger in the case where the refrigerant flows in the backwarddirection (see a black arrow in the drawing) than in the case where therefrigerant flows in the forward direction (see a white arrow in thedrawing).

FIG. 23 is an explanatory view illustrating the vortex type fluid diode72, in which (a) of FIG. 23 is the schematic perspective view, (b) ofFIG. 23 is a top view of (a) illustrating a flow of the refrigerant inthe forward direction, and (c) of FIG. 23 is a top view of (b)illustrating a flow of the refrigerant in the backward direction.

The vortex type fluid diode 72, as shown in (a) of FIG. 23, isconstructed of a vortex case 721 having a cylindrical vortex chamberformed therein, an axial nozzle 722 extended in a central axis directionof the vortex chamber in the vortex case 721, and a tangent nozzle 723extended in a tangential direction of an outer circumference of thevortex chamber.

In this vortex type fluid diode 72, in the case where the refrigerantflows from the upstream side to the downstream side of the refrigerantflow, as shown by white arrows in (b) of FIG. 23, the refrigerant fromthe axial nozzle 722 flows to the tangential nozzle 723 withoutdeveloping a vortex in the vortex chamber in the vortex case 721.

In contrast to this, in the case where the refrigerant flows from thedownstream side to the upstream side of the refrigerant flow, as shownby the black arrows in (c) of FIG. 23, the refrigerant from thetangential nozzle 723 flows vortically in the vortex chamber in thevortex case 721 and then flows into the axial nozzle 722. In this way,in the vortex type fluid diode 72, resistance becomes larger in the casewhere the refrigerant flows from the downstream side to the upstreamside of the refrigerant flow, that is, in the backward direction than inthe case where the refrigerant flows from the upstream side to thedownstream side of the refrigerant flow, that is, in the forwarddirection.

Other Embodiments

While the embodiments of the present disclosure have been describedabove, the present disclosure is not limited to these embodiments. Thepresent disclosure is not limited by the wording as claimed in therespective claims but includes a scope replaced easily from the claimsby persons skilled in the art as far as the scope does not depart fromthe scope as claimed in the claims and can have modifications addedthereto as appropriate, the modifications being made on the basis ofknowledge acquired by the persons skilled in the art. For example, thepresent disclosure can be modified variously in the following manner.

(A) In the respective embodiments described above, the magnetic fieldgenerating part of the magnetic field applying and removing device 32 isconstructed of the permanent magnets 323 a, 323 b. However, the magneticfield generating part is not limited to this but may be constructed ofan electric magnet for generating a magnetic field when current isapplied thereto.

(B) Like the respective embodiments described above, it is desirablethat the drive sources of the refrigerant pump 34 and the magnetic fieldapplying and removing device 32 are constructed of one electric motor35. However, the drive sources of the refrigerant pump 34 and themagnetic field applying and removing device 32 may be constructed ofseparate drive sources.

Further, like the ninth and the tenth embodiments, it is desirable thatthe drive sources of the respective valves 312 c, 313 c, 312 d, 313 dand the magnetic field applying and removing device 32 are constructedof one electric motor 35. However, the respective drive sources may beconstructed of separate drive sources.

(C) In the respective embodiments, the magnetic refrigeration system 2is applied to the vehicle air conditioning device 1. However, themagnetic refrigeration system 2 is not limited to this but may beapplied to the other device.

(D) The respective embodiments described above can be combined with eachother within a possible scope.

While the present disclosure has been described with reference topreferred embodiments thereof, it is to be understood that thedisclosure is not limited to the preferred embodiments andconstructions. The present disclosure is intended to cover variousmodification and equivalent arrangements. In addition, while the variouscombinations and configurations, which are preferred, other combinationsand configurations, including more, less or only a single element, arealso within the spirit and scope of the present disclosure.

1. A magnetic refrigeration system comprising: a cylindrical containerhaving a plurality of working chambers formed therein radially in acircumferential direction, the plurality of working chambers having amagnetic working material having a magnetocaloric effect arrangedtherein and having refrigerant flowing therethrough, the cylindricalcontainer having one and other refrigerant ports respectively on endfaces in a longitudinal direction; a magnetic field applying andremoving part which repeats applying and removing a magnetic field toand from the magnetic working material; a first refrigerant circulationcircuit constructed in such a way that the refrigerant flowing out of afirst refrigerant discharge part of the one refrigerant port flowsthrough a first heat exchanger and returns to a first refrigerantsuction part of the one refrigerant port; a second refrigerantcirculation circuit constructed in such a way that the refrigerantflowing out of a second refrigerant discharge part of the otherrefrigerant port flows through a second heat exchanger and returns to asecond refrigerant suction part of the other refrigerant port; and arefrigerant transfer part which transfers the refrigerant between theone refrigerant port and the other refrigerant port, wherein therefrigerant transfer part is constructed in such a way as to transferthe refrigerant from the other refrigerant port to the one refrigerantport after the magnetic field is applied to the magnetic workingmaterial by the magnetic field applying and removing part to therebymake the refrigerant flow out of the first refrigerant discharge part ofthe one refrigerant port to the first refrigerant circulation circuit,and in such a way as to transfer the refrigerant from the onerefrigerant port to the other refrigerant port after the magnetic fieldis removed from the magnetic working material by the magnetic fieldapplying and removing part to thereby make the refrigerant flow out ofthe second refrigerant discharge part of the other refrigerant port tothe second refrigerant circulation circuit, and a volume of a spaceconstructing each of the first refrigerant suction part, the firstrefrigerant discharge part, the second refrigerant suction part and thesecond refrigerant discharge part is smaller than a volume of therefrigerant discharged at one time in the refrigerant transfer part. 2.A magnetic refrigeration system comprising: a cylindrical containerhaving a plurality of working chambers formed therein radially in acircumferential direction, the plurality of working chambers having amagnetic working material having a magnetocaloric effect arrangedtherein and having refrigerant flowing therethrough, the cylindricalcontainer having one and other refrigerant ports respectively on endfaces in a longitudinal direction; a magnetic field applying andremoving part which repeats applying and removing a magnetic field toand from the magnetic working material; a first refrigerant circulationcircuit constructed in such a way that the refrigerant flowing out of afirst refrigerant discharge part of the one refrigerant port flowsthrough a first heat exchanger and returns to a first refrigerantsuction part of the one refrigerant port; a second refrigerantcirculation circuit constructed in such a way that the refrigerantflowing out of a second refrigerant discharge part of the otherrefrigerant port flows through a second heat exchanger and returns to asecond refrigerant suction part of the other refrigerant port; and arefrigerant transfer part which transfers the refrigerant between theone refrigerant port and the other refrigerant port, wherein after themagnetic field is applied to the magnetic working material by themagnetic field applying and removing part, the refrigerant transfer parttransfers the refrigerant from the other refrigerant port to the onerefrigerant port, and after the magnetic field is removed from themagnetic working material by the magnetic field applying and removingpart, the refrigerant transfer part transfers the refrigerant from theone refrigerant port to the other refrigerant port.
 3. The magneticrefrigeration system according to claim 2, further comprising: a suctionvalve provided to each of the first refrigerant suction part and thesecond refrigerant suction part and opened when the refrigerant issucked into the working chambers, and a discharge valve provided to eachof the first refrigerant discharge part and the second refrigerantdischarge part and opened when the refrigerant is discharged from theworking chambers.
 4. The magnetic refrigeration system according toclaim 3, wherein the discharge valve is arranged at a position nearer tothe working chambers than the suction valve is in the longitudinaldirection of the container.
 5. The magnetic refrigeration systemaccording to claim 3, wherein of the suction valve and the dischargevalve, at least the suction valve is constructed of a rotary valvehaving a valve plate and a rotary disk, the valve plate being arrangedadjacently to the working chambers and having a communication holecommunicating with interior of the working chambers, the rotary diskrotating in a circumferential direction of the container to thereby openor close the communication hole.
 6. The magnetic refrigeration systemaccording to claim 5, wherein the rotary valve is constructed in such away that the rotary disk rotates by power for driving the magnetic fieldapplying and removing part.
 7. The magnetic refrigeration systemaccording to claim 1, further comprising: a first backward flowpreventing part provided to each of the first refrigerant suction partand the first refrigerant discharge part of the one refrigerant port soas to allow the refrigerant to flow in one direction in order of thefirst refrigerant discharge part, a refrigerant flow-in port of thefirst heat exchanger, a refrigerant flow-out port of the first heatexchanger, and the first refrigerant suction part; and a second backwardflow preventing part provided to each of the second refrigerant suctionpart and the second refrigerant discharge part of the other refrigerantport so as to allow the refrigerant to flow in one direction in order ofthe second refrigerant discharge part, a refrigerant flow-in port of thesecond heat exchanger, a refrigerant flow-out port of the second heatexchanger, and the second refrigerant suction part.
 8. The magneticrefrigeration system according to claim 7, wherein at least one of thefirst backward flow preventing part and the second backward flowpreventing part is constructed of a fluid diode in which resistance issmaller in a forward direction of a flow of the refrigerant than in abackward direction of the flow of the refrigerant.
 9. The magneticrefrigeration system according to claim 2, wherein each of the firstrefrigerant suction part and the second refrigerant suction part is oneof a plurality of refrigerant suction parts disposed in correspondenceto the plurality of working chambers, each of the first refrigerantdischarge part and the second refrigerant discharge part is one of aplurality of refrigerant discharge parts disposed in correspondence tothe plurality of working chambers, the plurality of refrigerant suctionparts are positioned on a same circumference when viewed from thelongitudinal direction of the container, and the plurality ofrefrigerant discharge parts are positioned on a same circumference whenviewed from the longitudinal direction of the container.
 10. Themagnetic refrigeration system according to claim 2, wherein the magneticfield applying and removing part is constructed of a magnetic fieldgenerating part, a rotary shaft which rotatably supports the magneticfield generating part and a drive part which drives the rotary shaft,and the magnetic field generating part is disposed in such a way as toperiodically come near to the magnetic working material according torotation of the rotary shaft.
 11. The magnetic refrigeration systemaccording to claim 10, further comprising: a power transmissionmechanism which transmits power by the drive part to the refrigeranttransfer part, wherein the refrigerant transfer part reciprocallytransfers the refrigerant between the one refrigerant port and the otherrefrigerant port by the power transmitted via the power transmissionmechanism.
 12. The magnetic refrigeration system according to claim 2,wherein the refrigerant transfer part is constructed of a multi-cylindertype piston pump having a plurality of cylinders and a plurality ofpistons so as to correspond to the plurality of working chambers.
 13. Avehicle air conditioning device to which the magnetic refrigerationsystem according to claim 2 is applied, the vehicle air conditioningdevice comprising: a case constructing an air flow passage for blown airto be blown into a passenger compartment, wherein the first heatexchanger is arranged in the case to construct a heating heat exchangerthat heats the blown air, and wherein the second heat exchanger isarranged in the case to construct a cooling heat exchanger that coolsthe blown air.
 14. The vehicle air conditioning device according toclaim 13, wherein the first heat exchanger is arranged downstream of thesecond heat exchanger in a flow of the blown air in the case.
 15. Thevehicle air conditioning device according to claim 13 furthercomprising: a temperature adjusting part which adjusts a volume of theblown air flowing into the first heat exchanger to thereby adjust atemperature of air blown off into the passenger compartment.